CN201666343U - Differential used as dynamic coupling device of series parellel hybrid electric vehicle - Google Patents

Abstract

The utility model discloses a differential used as a dynamic coupling device of a series parellel hybrid electric vehicle, which solves the problems of slip and friction between planetary gears (3) and planetary gear shafts (4). The differential comprises a differential shell (1), axle shaft gears (2), the planetary gears (3), the planetary gear shafts (4), bearing caps (5), rolling bearings (6) and gaskets (7), wherein one end of each planetary gear shaft (4) is arranged in the shaft hole of each planetary gear (3); the planetary gear shafts (4) and the shaft holes of the planetary gears (3) are in interference fit; the other end of the planetary gear shaft (4) is arranged in the upper hole and the lower hole of the differential shell (1) through a pair of rolling bearings (6); the axes of rotation of the two planetary gear shafts (4) are colinear and vertically intersect with the axes of rotation of the axle shaft gears (2); the bearing caps (5) and the gaskets (7) are fixed on the end surfaces of the bosses of the outer ends of the upper hole and the lower hole of the differential shell (1); and gaps are arranged between the backs of the planetary gears (3) and the inner wall of the differential shell (1).

Description

Differential mechanism as series parallel hybrid power vehicle power coupling device

Technical field

The utility model relates to a kind of dynamic coupling device, and more particularly, the utility model relates to a kind of differential mechanism as series parallel hybrid power vehicle power coupling device.

Background technique

Current environmental pollution and energy shortage problem are serious day by day, and it is more and more urgent with the requirement that improves exhaust emissions that automobile is reduced fuel consume, so electric vehicle engineering progressively becomes the trend of automotive research and exploitation.But since present stage battery technology not mature enough, the development of pure electric automobile (EV) has been subjected to very big restriction with development.Mixed power electric car (HEV---Hybrid Electric Vehicle, generally refer to the oil electric mixed dynamic automobile) worldwide be subjected to approving widely in the potentiality aspect solution environmental protection and the energy problem as the transiting product between traditional fuel-engined vehicle and the pure electric automobile, not only become the focus in the automobile power research, also become a lot of auto vendors instantly with the emphasis of future development.

Current commonplace hybrid vehicle scheme is to adopt motor and motor, generator to make up.How realizing the power distribution between hybrid electric vehicle engine and motor, the generator, is one of development hybrid vehicle key issue that must solve.

Utilize the dynamic coupling device of differential mechanism as Hybrid Vehicle, can realize hybrid vehicle continuous type series parallel connection drive form, rotating speed, torque by regulator generator can make engine operation at best efficiency point, thoroughly solve conventional engines because the problem of the operation point inefficiency that causes with the mechanical connection of wheel, thereby realized the control performance of electronic stepless continuous speed change (ECVT).Utilize the motor of high torque (HT) characteristic to realize the increase torque function of traditional speed changer, can eliminate mechanisms such as speed changer, clutch, the car load power transmission system is greatly simplified.By reasonable control generated output power, can realize the function of real-time regulated battery SOC (state of charge) in the driving process.

Because the planetary pinion rotation rotating speed of automobile tradition differential mechanism is less, and run duration is shorter, therefore no any connected element between the planetary pinion of automobile tradition differential mechanism and the planet pin, the sliding wear when only depending between the two ransaxle lubricant oil to improve its relative movement.The lubricating method that is proposed at present comprises: suitably increase the matching gap of differential mechanism component, increase the pressure angle on hole and the axle Line of contact, form effective wedge gap, promote oil abrasion to form; On differential gear, planetary pinion and planet axis, increase oil duct, make the rapid engaging friction of the oil droplet that splashes surface, constitute lubricated preferably environment; Gear shaft is carried out phosphatization handle, guarantee initial lubricated break-in; Install fluid delivery system additional, utilize the controllable pressure controlling mechanism that differential mechanism is lubricated; Lubricating oil bath is set, guarantees lubricated.

But when traditional differential mechanism is used as power coupling apparatus of hybrid power vehicle, there is big speed discrepancy all the time in output semiaxis about it, differential pinion gear and planet pin rely on above-mentioned lubricating method can only keep relatively rotating of short time, otherwise serious sliding wear between the two can appear, cause the incorrect engagement of differential pinion gear and differential gear, even gear teeth damage appears, not only greatly reduces the life-span of differential mechanism, and influences the normal transmission of power of automobile.Lubrication problem when all differential mechanism not being used as power coupling apparatus of hybrid power vehicle in the present patent documentation proposes a solution.

Summary of the invention

Technical problem to be solved in the utility model is the sliding wear problem that has overcome between differential pinion gear and the planet pin, and a kind of differential mechanism as series parallel hybrid power vehicle power coupling device that adopts measure such as rolling bearing is provided.

For solving the problems of the technologies described above, the utility model is to adopt following technological scheme to realize: described differential mechanism as series parallel hybrid power vehicle power coupling device includes differential casing, differential gear that two structures are identical, the planetary pinion that two structures are identical, the planet pin that two root architectures are identical, two bearing cap, two pairs of rolling bearings and two pads that structure is identical that model is 7004C that structure is identical.

Packing in the axis hole on the identical planetary pinion of two structures in the inner end of the planet pin that two root architectures are identical, is that interference fit connects between the axis hole on the identical planetary pinion of the planet pin that two structures are identical and two structures.The outer end of the planet pin that two root architectures are identical is that the rolling bearing of 7004C is packed in the upper shaft hole and lower shaft hole of differential casing by a pair of model respectively.The rotational axis of the rotational axis conllinear of the planet pin that two root architectures are identical and the differential gear identical with two structures intersects vertically, and the identical pad of two structures bearing cap identical with two structures is fixedly mounted on the end face of the upper shaft hole of differential casing and lower shaft hole outer end boss successively by bolt.

Be provided with the gap of 0.5-1.0mm between the planetary back side that two structures described in the technological scheme are identical and the differential casing inwall; The outer end of the planet pin that described two root architectures are identical is that the rolling bearing of 7004C is packed into and is meant in the upper shaft hole of differential casing and the lower shaft hole by a pair of model respectively: each is that the rolling bearing of 7004C is one positive one instead to be sleeved on the outer end of planet pin and to reinstall in the upper shaft hole and lower shaft hole of differential casing to model, and each is that the interior ring of rolling bearing of 7004C and the outer end of planet pin are that interference fit is connected to model; One side of the bearing cap that described two structures are identical is provided with the annulus boss, be evenly equipped with bolt hole around the annulus boss, the end face of the annulus boss of bearing cap one side that two structures are identical respectively with the upper shaft hole of differential casing and lower shaft hole in the outer shroud end face of rolling bearing in the outside contact and be connected.

Compared with prior art the beneficial effects of the utility model are:

Only traditional differential mechanism is carried out the partial structurtes transformation, just realize differential mechanism is used as the dynamic coupling device of hybrid vehicle, played the effect of getting twice the result with half the effort, simplified the brand-new design and the trial-production of power coupling apparatus of hybrid power vehicle greatly, save time, save expense.

Description of drawings

Below in conjunction with accompanying drawing the utility model is further described:

Fig. 1 be measures such as expression employing rolling bearing described in the utility model etc. as the whole-cutaway view on the plan view of the differential design of series parallel hybrid power vehicle power coupling device;

Fig. 2 is the expression free-body diagram as the planet pin in the differential mechanism of series parallel hybrid power vehicle power coupling device described in the utility model;

Among the figure: 1. differential casing, 2. differential gear, 3. planetary pinion, 4. planet pin, 5. bearing cap, 6. rolling bearing, 7. pad.

Embodiment

Below in conjunction with accompanying drawing the utility model is explained in detail:

For solving the sliding wear problem between differential spider pinion shaft hole and the planet pin, the Chinese invention patent publication number is CN 101482166A, open day is on February 10th, 2009, invention and created name is " as the differential mechanism of power coupling apparatus of hybrid power vehicle ", in this case traditional differential mechanism is carried out the partial structurtes transformation, the friction law of assembling needle roller when improving that both are relative to run up between the axis hole of differential pinion gear and planet pin.

But described patent of invention has just been improved the axis hole of differential pinion gear and the friction law between the planet pin, does not relate to the improvement of friction law between the planetary pinion back side and the differential casing.In the actual experiment process, a large amount of heats of the friction-produced between the planetary pinion back side and the differential casing also the sliding wear phenomenon occurs.

For solving the problem that described patent of invention exists, the utility model adopts the axis hole interference fit of planet pin 4 and planetary pinion 3, and be installed in the hole on the differential casing 1 by rolling bearing 6, wherein bearing cap 5 limits moving axially of rolling bearings 6, especially restrictions planetary gear 3 moving to bearing cap 5 directions; By adjusting pad 7, can control the distance between planetary pinion 3 back sides and the inner walls, make between planetary pinion 3 back sides and the differential casing inwall and leave the 0.5-1.0mm gap, avoided between planetary pinion 3 and the planet pin 4, the friction law during running up relatively between the back side of planetary pinion 3 and the inner walls.

The principle that is used as the differential mechanism of series parallel hybrid power vehicle power coupling device according to rotating speed differential, torque mean allocation described in the utility model, make its input shaft connect motor, two output shafts connect motor and generator respectively, generator for electricity generation is exported in half torque of engine power output, second half torque actuated wheel, the continuous type series parallel connection drive form of realization hybrid vehicle.Described function sees for details in Chinese invention patent, and the patent No. is CN 200710055306.7, and open day is on February 18th, 2008, and invention and created name is " dynamic coupling device of Hybrid Vehicle ".

Differential mechanism as series parallel hybrid power vehicle power coupling device described in the utility model mainly is made up of with two pairs of identical rolling bearings 6 of structure the planet pin 4 of differential casing 1, two differential gears that structure is identical 2, two planetary pinions that structure is identical 3, weak point that two root architectures are identical, two bearing caps that structure is identical 5.

Consult Fig. 1, differential mechanism as series parallel hybrid power vehicle power coupling device described in the utility model replaces with a long planet gear axle of prior art the planet pin 4 of the identical weak point of two root architectures, one end of the planet pin 4 of the weak point that two root architectures are identical is packed in the axis hole on the identical planetary pinion 3 of two structures, is that interference fit connects between the axis hole on an end (inner end) of the planet pin 4 of the weak point that two root architectures the are identical planetary pinion 3 identical with two structures.The other end (outer end) of the planet pin 4 of the weak point that two root architectures are identical is that the rolling bearing 6 of 7004C is packed in the upper shaft hole and lower shaft hole on the differential casing 1 by a pair of model respectively, is sleeved on the planetary pinion 3 of planet pin 4 inner ends and the differential gears 2 that are sleeved on two output semiaxis, one end in the differential casing 1 and is meshed.A pair of model is that the rolling bearing 6 of 7004C is one positive one instead to be sleeved on the cylndrical surface of the other end (outer end) of planet pin 4, and each is that the outer end (cylndrical surface) of the interior ring of rolling bearing 6 and the planet pin 4 of 7004C is connected for interference fit to model.The rotational axis conllinear of the planet pin 4 of the weak point that two root architectures after the installation are identical and and two output semiaxis intersect vertically, exactly and be sleeved on two rotational axis of exporting the identical differential gear 2 of two structures on the semiaxis and intersect vertically.The identical bearing cap 5 of two structures is installed in by bolt on the end face of outer end boss of upper shaft hole on the differential casing 1 and lower shaft hole, and pad 7 is adjusted in adding between the outer end raised head face on bearing cap 5 and the differential casing 1, for ease of two bearing caps 5 that structure is identical are installed, earlier be used for installing the upper shaft hole of planet pin 4 of the identical weak point of two root architectures and the position of lower shaft hole casts out boss in differential casing 1 processing, then last, the upper shaft hole and the lower shaft hole of the planet pin 4 of the weak point that installation and processing two root architectures are identical on the lower convex platform, the aperture of upper shaft hole and lower shaft hole of planet pin 4 that the identical weak point of two root architectures is installed is bigger than the aperture of the upper shaft hole of the middle installation of prior art (above-mentioned patent) planet pin and lower shaft hole, so that be the planet pin 4 that the rolling bearing 6 of 7004C is installed the identical weak point of two root architectures by a pair of model.One side of the bearing cap 5 that described two structures are identical is provided with the annulus boss, be evenly equipped with bolt hole around the annulus boss, the end face of the annulus boss of bearing cap 5 one sides that two structures are identical respectively with the upper shaft hole of differential casing 1 and lower shaft hole in the outer part the outer shroud end face of rolling bearing 6 contact and be connected.Play restriction and be sleeved on the moving axially of rolling bearing 6 that a pair of model on planet pin 4 outer ends of the identical weak point of two root architectures is 7004C.By adjusting pad 7, can control the distance between planetary pinion 3 back sides and differential casing 1 inwall, make between planetary pinion 3 back sides and differential casing 1 inwall and leave the 0.5-1.0mm gap, avoided between planetary pinion 3 and the planet pin 4, the friction law during running up relatively between the back side of planetary pinion 3 and differential casing 1 inwall.

By above-mentioned Transform Type design, the serious sliding wear problem of having avoided between planetary pinion 3 and the planet pin 4, having occurred owing to friction when running up relatively between the back side of planetary pinion 3 and the differential casing 1; The planetary pinion 3 of having avoided differential mechanism and the incorrect engagement of differential gear 2 even occur that the gear teeth damage and life-span of causing not only greatly reducing differential mechanism, and influence the generation of the normal transmission of power phenomenon of automobile.

The rolling bearing type selecting:

According to force analysis, rolling bearing 6 need bear the axial force of planetary pinion 3, and radial force is in the moment of flexure of rolling bearing 6 places generation.Change minimum principle in conjunction with planet pin 4 and differential casing 1 physical dimension again, selecting the model of rolling bearing 6 is the angular contact roller bearing of 7004C, and installs in pairs back-to-back (one positive one is anti-).

The rolling bearing life verification:

Consult Fig. 2, analyze the stressed of planet pin.Because differential casing 1 torque T _jEffect, the corresponding tangential force in differential casing 1 two ends is F ₀, and T _j=F ₀L ₀(F ₀, L ₀All do not draw L among the figure ₀Be the distance between the force bearing point of two ends, unit: mm).Simultaneously, planet pin 4 is bearing the tangential force F from planetary pinion 3 at work _r

According to equalising torque:

F _rL＝F ₀L ₀＝T _j

So:

$F_r=\frac{T_j}{L}$

In the formula:

T _j-be delivered to torque on the differential casing 1 by the driven planetary pinion of main reducing gear, unit: Nm, the utility model motor 1 moment of torsion is directly imported the differential coupled system, so T _j=102, unit: Nm.

The radial force F that two planetary pinions of L-produce _rPoint of force application between distance, 63mm.

So:

$F_r=\frac{102N\·m}{63\mathrm{mm}}=1619N$

According to planetary engaging force relation

F _a＝F _r?tanαsinδ＝545.6N

In the formula:

α-planetary pressure angle, 22.5 °

δ-planetary pitch cone angle, 35.53 °

The Performance Calculation of table 1 (tapered roller) rolling bearing

According to " mechanical design handbook " middle (center) bearing Calculation for life formula, the verification needle roller life-span:

$L_{10h}=\frac{{10}^6}{60n}{\left(\frac{C_r}{P}\right)}^{\mathrm{\ϵ}}$

In the formula:

L _10hThe working life of-bearing, h

C _rThe dynamic load rating of-bearing, N.Look into handbook, C _r=25kN

The equivalent dynamic load of P-bearing, N.The listed P of table 1 ₁, P ₂In bigger, i.e. P=P ₁=6337.8N

The rotating speed of n-bearing, r/min

ε-life index, roller bearing, ε=10/3

The rotation speed n of bearing, i.e. planet gear speed of autorotation by differential mechanism is carried out the rotation speed relation analysis, has:

$n=\mathrm{\&Delta;<figure-callout\; id="2"\; label="n\; Z"\; filenames="HSA00000055170100011.png"\; state="\{\{state\}\}">n</figure-callout>}\frac{Z_{}}{}\frac{{}_2}{2{\mathrm{<figure-callout\; id="1"\; label="Z"\; filenames="HSA00000055170100011.png"\; state="\{\{state\}\}">Z</figure-callout>}}_1}$

In the formula:

Δ n-two-semiaxle gear rotational speed is poor, r/min

Z ₁-planetary pinion the number of teeth

Z ₂-differential gear the number of teeth

Poor according to two-semiaxle gear mean speed, the average speed of autorotation of calculating planetary pinion is:

$n=\mathrm{\&Delta;<figure-callout\; id="1"\; label="n\; Z"\; filenames="HSA00000055170100011.png"\; state="\{\{state\}\}">n</figure-callout>}\frac{Z_{}}{}\frac{{}_1}{2{\mathrm{<figure-callout\; id="2"\; label="Z"\; filenames="HSA00000055170100011.png"\; state="\{\{state\}\}">Z</figure-callout>}}_2}=1022.6\frac{14}{2\&times;10}=715.8r/\min$

Finally, calculating rolling bearing life is:

$L_{10h}=\frac{{10}^6}{60n}{\left(\frac{C_r}{P}\right)}^{\mathrm{\&epsiv;}}=2258$ Hour

But the utility model is intended to illustrate the feasibility of differential coupled system and modification in construction thereof, and only verifies in the test stand aspect.Because the relative automobile running time of bench time is much shorter, so current differential mechanism rolling bearing life can satisfy test requirements document.If technological scheme described in the utility model is to Industry Promotion, the then above-mentioned life-span checks and can be enterprise the analysis foundation of remodeling and bearing selection from now on is provided.

The planet pin design:

According to the dimensional parameters of original differential mechanism, the diameter of planet pin is φ 20, adopts raw material: 20CrMnTi.

Owing to behind the planet pin remodeling, become present overhang, must carry out tension and compression, the check of crooked combined strength to the planet pin 4 after the remodeling by original simply supported beam.

The point of action of the power of rolling bearing 1, i.e. the tension and compression at section variation place, crooked combined stress σ are:

$\mathrm{\&sigma;}={\mathrm{\&sigma;}}_l+{\mathrm{\&sigma;}}_w=\frac{F_{a1}}{A}\frac{M}{W}=\frac{4f_{a1}}{{\mathrm{\&pi;<figure-callout\; id="2"\; label="d"\; filenames="HSA00000055170100011.png"\; state="\{\{state\}\}">d</figure-callout>}}^2}+\frac{32F_r(L^{\&prime;}-a)}{{\mathrm{\&pi;<figure-callout\; id="3"\; label="d"\; filenames="HSA00000055170100011.png"\; state="\{\{state\}\}">d</figure-callout>}}^3}=54.26\mathrm{MPa}$

In the formula:

M-calculates the suffered moment of flexure of section part planet pin, Nm

The bending resistant section coefficient of W-axle,

D-planetary pinion shaft diameter, mm.

Through tabling look-up the allowable stress of 20CrMnTi low-carbon alloy steel [σ]=291～315MPa.As seen, Zhou tension and compression, crooked combined strength meet the demands.

To sum up, although planet pin 4 moments of flexure behind the remodeling become big and are subjected to axial force, turn round parts and directly act on differential mechanism because Engine torque increases without any deceleration, so the planet pin behind the remodeling satisfies requirement of strength fully.

Planetary pinion flank of tooth contact fatigue strength is checked:

Because planetary pinion often only plays the equiarm track bar in the work of automobile differential, therefore differential gear is mainly carried out flexural strength and calculate, to then not considering fatigue life.But when as the mixed power coupled system,, check so must carry out fatigue strength to planetary pinion owing to there is bigger speed discrepancy always.

For bevel gear, and two bevel gear axis angle of cut ∑=90 are when spending according to " mechanical design handbook ", and flank of tooth contact fatigue strength is:

${\mathrm{\&sigma;}}_H=\sqrt{\frac{F_t{K}_A{K}_V{K}_{\mathrm{H\&beta;}}{K}_{\mathrm{H\&alpha;}}\sqrt{{\mathrm{<figure-callout\; id="2"\; label="u"\; filenames="HSA00000055170100011.png"\; state="\{\{state\}\}">u</figure-callout>}}^2+1}}{0.85b{d}_{m1}u}}\&times;Z_H{Z}_E{Z}_{\mathrm{\&epsiv;\&beta;}}{Z}_K$

Wherein: K _A-coefficient of utilization; K _V-Dynamic factor.F _tThe tangential force of-planetary pinion mid point standard pitch circle; K _{H β}-teeth directional load distribution coefficient; K _{H α}-between cog load distribution coefficient;

The b-facewidth; d _M1The average standard pitch diameter of-planetary pinion; Z _H-node region coefficient; Z _E-elasticity coefficient; Z _{ε β}-contact ratio coefficient.Z _K-bevel gear coefficient.

Allowable contact stress:

${\mathrm{\&sigma;}}_{\mathrm{HP}}=\frac{{\mathrm{\&sigma;}}_{\mathrm{Hlim}}}{S_{H\min }}\&times;Z_N{Z}_{\mathrm{LvR}}{Z}_X{Z}_W$

Wherein, σ _HlimThe contact fatigue strength limit of-test gear; S _Hmin-safety coefficient; Z _N-Life factor, Z _LvR-lubricant film influence coefficient; Z _X-Size factor; Z _W-work hardening coefficient.

Because the precision prescribed of automobile differential gear tooth is lower, so the extensive use of finish forge differential gear process quilt.According to investigation, the machining accuracy parameter of automobile differential planet, differential gear is at present: tooth-face roughness Ra0.8, grade of accuracy 8-GB11365.In conjunction with planetary machining accuracy grade,, calculate flank of tooth contact fatigue strength σ according to relevant planetary pinion physical dimension formula and method _H=1766MPa, allowable contact stress σ _HP=1710MPa, as seen, σ _H＞σ _HP(flank of tooth contact fatigue strength surpass slightly border allowable contact stress 3%), promptly, can not satisfy planetary pinion requirement fatigue life of HEV differential coupled system fully with current planetary processing method and machining accuracy because there is higher rotation speed in the planetary pinion of differential coupled system.

But the utility model is intended to illustrate the feasibility of differential coupled system and modification in construction thereof, and only verifies in the test stand aspect.Because the relative automobile running time of bench time is much shorter, so current differential pinion gear can satisfy test requirements document fatigue life.If the utility model achievement can be to Industry Promotion through checking, then above-mentioned strength check can be enterprise remodeling and accurately machined analysis foundation from now on is provided.

The analysis showed that by above-mentioned, traditional differential mechanism is carried out structure of modification, interference fit between differential spider pinion shaft one end and planetary pinion, the other end is installed on the differential carrier by rolling bearing.Planetary pinion that occurs in the time of can solving traditional differential mechanism as the hybrid vehicle dynamic coupling system and the friction problem between the planet pin, and the serious sliding wear problem between the planetary pinion back side and the differential casing in original invention, avoided the loss of automobile power transmission efficiency and the minimizing in differential mechanism working life.

Claims (4)

1. differential mechanism as series parallel hybrid power vehicle power coupling device, mainly form with two identical planetary pinions (3) of structure by differential casing (1), two identical differential gears (2) of structure, it is characterized in that described differential mechanism as series parallel hybrid power vehicle power coupling device also includes the identical planet pin of two root architectures (4), two bearing cap (5), two pairs of rolling bearings (6) and two pads (7) that structure is identical that model is 7004C that structure is identical;

Pack in the axis hole on the identical planetary pinion (3) of two structures in the inner end of the planet pin that two root architectures are identical (4), between the axis hole on the identical planetary pinion (3) of the planet pin (4) that two structures are identical and two structures is that interference fit connects, the outer end of the planet pin that two root architectures are identical (4) is that the rolling bearing (6) of 7004C is packed in the upper shaft hole and lower shaft hole of differential casing (1) by a pair of model respectively, the rotational axis of the rotational axis conllinear of the planet pin that two root architectures are identical (4) and the differential gear (2) identical with two structures intersects vertically, and the identical pad (7) of two structures bearing cap (5) identical with two structures is fixedly mounted on the end face of the upper shaft hole of differential casing (1) and lower shaft hole outer end boss successively by bolt.

2. according to the described differential mechanism of claim 1 as series parallel hybrid power vehicle power coupling device, it is characterized in that, be provided with the gap of 0.5-1.0mm between the back side of the planetary pinion (3) that described two structures are identical and differential casing (1) inwall.

3. according to the described differential mechanism of claim 1 as series parallel hybrid power vehicle power coupling device, it is characterized in that, the outer end of the planet pin (4) that described two root architectures are identical is that the rolling bearing (6) of 7004C is packed into and is meant in the upper shaft hole of differential casing (1) and the lower shaft hole by a pair of model respectively: each is that the rolling bearing (6) of 7004C is one positive one instead to be sleeved on the outer end of planet pin (4) and to reinstall in the upper shaft hole and lower shaft hole of differential casing (1) to model, and each is that the interior ring of rolling bearing (6) of 7004C and the outer end of planet pin (4) are that interference fit is connected to model.

4. according to the described differential mechanism of claim 1 as series parallel hybrid power vehicle power coupling device, it is characterized in that, one side of the bearing cap (5) that described two structures are identical is provided with the annulus boss, be evenly equipped with bolt hole around the annulus boss, the end face of the annulus boss of bearing cap (5) one sides that two structures are identical respectively with the upper shaft hole of differential casing (1) and lower shaft hole in the outer shroud end face of rolling bearing (6) in the outside contact and be connected.

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