CN104191954A - Planetary type dual-mode petrol-electric parallel and serial hybrid power system - Google Patents
Planetary type dual-mode petrol-electric parallel and serial hybrid power system Download PDFInfo
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- CN104191954A CN104191954A CN201410468230.0A CN201410468230A CN104191954A CN 104191954 A CN104191954 A CN 104191954A CN 201410468230 A CN201410468230 A CN 201410468230A CN 104191954 A CN104191954 A CN 104191954A
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
Abstract
The invention discloses a planetary type dual-mode petrol-electric parallel and serial hybrid power system. The problem that a parallel and serial hybrid power system requires a large motor is solved. The planetary type dual-mode petrol-electric parallel and serial hybrid power system comprises an engine, a first motor, a dual-clutch, a second motor, an output shaft, a front planet raw and a rear planet raw, wherein the front planet raw sleeves the right end of an output shaft of the engine; a right end of a gear ring of the front planet row sleeves the left end of the output shaft; the dual-clutch sleeves the right end of the output shaft; the left end of a left pressure plate of the dual-clutch is connected with the right end of the gear ring of the front planet row via a spline pair; the second motor is arranged on the output shaft on the right side of the dual-clutch; the rear planet row is arranged on the output shaft on the right side of the second motor; the right end of a shaft sleeve of the dual-clutch is connected with the left end of the second motor via a spline pair; the right end of the second motor is connected with the left end of a sun gear of the rear planet row via a spline pair; the first motor sleeves the output shaft, which is arranged on the left side of the front planet row, of the engine; and the right end of the first motor is connected with the left end of a sun gear in the front planet row via a spline pair.
Description
Technical field
The present invention relates to a kind of power system of hybrid vehicle, or rather, the present invention relates to the electric parallel-serial hybrid power system of a kind of planetary bimodulus oil.
Background technology
Along with the urgent of energy problem with to the improving constantly of environmental protection requirement, energy-saving and environmental protection become the inevitable requirement of future automobile development.Hybrid vehicle is actv. energy-saving automobile scheme at present, and its drive system has series, parallel and three kinds of forms of series-parallel connection.Tandem energy is realized the optimal control of driving engine, but all energy all can, through secondary conversion, lose larger; Parallel connection can realize good driving efficiency, but driving engine and output shaft mechanical connection can not ensure that driving engine is all the time in work area preferably; Series-parallel connection can, in conjunction with the advantage of series and parallel connections, be evaded the shortcoming of the two, is the configuration scheme of optimizing the most in three.
Current Series-Parallel HEV mainly adopts planetary mechanism as power dividing device, and typical version comprises (Toyota Hybird System) the THS system of Toyota and general (Allison Hybrid System) AHS system.Wherein, the THS system of Toyota adopts single planetary row structure, belong to single mode power dividing device, it can only realize a kind of pattern of input type power dividing, the advantage of this THS system is in realizing electronic infinite variable speed (EVT) function, have simple structure, control relatively easy.But the gear ring of THS system is directly connected to output shaft, its dependence to motor is larger, for good dynamic property is provided, need in system, select power grade and the larger motor of output torque, this has increased the degree of difficulty of integral vehicle cost and installation to a great extent.In addition, THS system is owing to can only realizing a kind of pattern of input type power dividing, and its driving efficiency in high velocity is less.The AHS system of General Corporation adopts double or three rows of planetary mechanisms to realize power dividing, can realize two kinds of patterns of input type power dividing and combined type power dividing, because mutually making up of two kinds of patterns, make the driving efficiency of AHS can maintain higher level in whole speed of a motor vehicle region, this point AHS is better than THS, switch but the control that often needs multiple power-transfer clutchs in AHS system carrys out implementation pattern, this makes the structure of whole system very complicated, controls difficulty and has also increased a lot.
Summary of the invention
Technical matters to be solved by this invention is that to have overcome current parallel-serial hybrid power automobile large to motor dependence, needs large motor that the problem of enough propulsive effort is provided, and provides a kind of planetary bimodulus oil electric parallel-serial hybrid power system.
For solving the problems of the technologies described above, the present invention adopts following technical scheme to realize: the described electric parallel-serial hybrid power system of planetary bimodulus oil includes driving engine, inverter, super capacitor, No. two inverters, motor, double-clutch, No. two motors, output shaft, front planet row and rear planet rows.
Front planet row is sleeved on the right-hand member of engine output shaft of driving engine for being rotationally connected, the right-hand member of the front planet toothrow circle in front planet row is sleeved on the first paragraph axle of output shaft as being rotationally connected, double-clutch is sleeved on the output shaft on front planet row cover right side, the left end of the left platen in double-clutch is that spline pair is connected with the right-hand member of front planet toothrow circle, No. two motors are arranged on the output shaft on double-clutch right side as being rotationally connected, rear planet row is arranged on the output shaft on No. two motor right sides, axle sleeve right-hand member in double-clutch is that spline pair is connected with the left end of the hollow shaft of No. two motors, the right-hand member of the hollow shaft of No. two motors is that spline pair is connected with the left end of the rear planet row sun wheel in rear planet row, motor is sleeved on the engine output shaft in front planet row left side as being rotationally connected, and the right-hand member of the hollow shaft of a motor is that spline pair is connected with the left end of the front planet row sun wheel in front planet row.
Three joints of a motor described in technical scheme connect respectively three alternating current I/O joint x, y, z of an inverter by cable, three joints of No. two motors adopt cable to be connected with three alternating current I/O joint x ', y ', z ' of No. two inverters respectively, and the positive and negative connector of an inverter and No. two inverters adopts respectively cable to be connected with the both positive and negative polarity of super capacitor.
Double-clutch described in technical scheme also comprises casing, right platen, the active friction plate that 6 chip architectures are identical, driven friction disk, left clutch hub, right clutch hub and the axle sleeve that 6 chip architectures are identical.
Described left platen and right platen are arranged in casing, between left platen and right platen, be fixed together by screw, left clutch hub and right clutch hub are arranged in the annular chamber between left platen and right platen, active friction plate that 6 chip architectures the are identical driven friction disk identical with 6 chip architectures alternately and be divided into two groups, one group of active friction plate and driven friction disk are arranged in the annular chamber between left platen and left clutch hub, another group active friction plate and driven friction disk are arranged in the annular chamber between right clutch hub and right platen, the active friction plate that 6 chip architectures are identical adopts spline pair to be connected with the two ends of left platen inner ring surface, the driven friction disk that 6 chip architectures are identical adopts spline pair to be connected with left clutch hub with the outer ring surface of the ring shaped axial boss of right clutch hub, left clutch hub is connected with axle sleeve with output shaft by spline pair successively with right clutch hub.
Axle sleeve described in technical scheme is sleeved on the optical axis on output shaft shaft shoulder right side, between the optical axis on the two ends of axle sleeve and output shaft shaft shoulder right side, plain bearing is installed, the right side of the left side of axle sleeve and the output shaft shaft shoulder is sliding block joint, left platen is sleeved on the second segment axle of output shaft, between the second segment axle of left platen and output shaft, bearing shell is installed, the second segment axle of bearing shell and output shaft is interference fit, it between left platen and bearing shell, is free-running fit, on the external cylindrical surface that left platen contacts with casing inner ring surface, be provided with seal groove, seal ring (33) is installed in seal groove.
Front planet row described in technical scheme also comprises front planetary line, 4 front planet rows of planetary wheel, 4 front planet rows of planetary wheel bearing pin and front planetary line left side rolling discs that structure is identical that structure is identical.4 identical front planet rows of planetary wheel bearing pins of structure are arranged on front planetary line and front planetary line left side rolling disc, the rotation axis of the front planet rows of planetary wheel bearing pin that 4 structures are identical is on the circumference of the radiuses such as the rotation axis of rolling disc on the left of front planetary line and front planetary line, 4 identical front planet rows of planetary wheels of structure are sleeved on 4 identical front planet rows of planetary of structure and take turns on bearing pin as being rotationally connected, outside tooth and the front planet toothrow circle of the front planet rows of planetary wheel that 4 structures are identical are connected with a joggle, inner tines and the front planet row sun wheel of the front planet rows of planetary wheel that 4 structures are identical are connected with a joggle.
The front planet rows of planetary that the identical front planet rows of planetary wheel of 4 structures described in technical scheme is identical with 4 structures is taken turns between bearing pin 4 bearing pin sleeves that structure is identical is installed, on the identical front planet rows of planetary wheel bearing pin of 4 structures between the front planetary line left side rolling disc front planet rows of planetary wheel identical with 4 structures, being set with 4 identical pads of structure is contact connection, on the identical front planet rows of planetary wheel bearing pin of 4 structures between the front planetary line front planet rows of planetary wheel identical with 4 structures, being set with a pad that other 4 structures are identical connects for contact, the two ends of front planet row sun wheel endoporus are provided with a bearing shell and No. two bearing shells.
Rear planet row described in technical scheme also comprises rear planet row gear ring, rear planet row pinion carrier, 4 rear planet row satellite gear, 4 rear planet row satellite gear bearing pin and rear planet row pinion carrier left side rolling discs that structure is identical that structure is identical.4 identical rear planet row satellite gear bearing pins of structure are arranged on rear planet row pinion carrier and rear planet row pinion carrier left side rolling disc, the rotation axis of the rear planet row satellite gear bearing pin that 4 structures are identical is on the circumference of the radiuses such as rolling disc rotation axis on the left of rear planet row pinion carrier and rear planet row pinion carrier, 4 identical rear planet row satellite gears of structure are sleeved on the rear planet row satellite gear bearing pin that 4 structures are identical as being rotationally connected, outside tooth and the rear planet row gear ring of the rear planet row satellite gear that 4 structures are identical are connected with a joggle, inner tines and the rear planet row sun wheel of the rear planet row satellite gear that 4 structures are identical are connected with a joggle.
Between the identical rear planet row satellite gear bearing pin of the rear planet row satellite gear that 4 structures described in technical scheme are identical and 4 structures, 4 No. two bearing pin sleeves that structure is identical are installed, on the identical rear planet row satellite gear bearing pin of 4 structures between the rear planet row pinion carrier left side rolling disc rear planet row satellite gear identical with 4 structures, being set with 4 No. two identical pads of structure is contact connection, on the identical rear planet row satellite gear bearing pin of 4 structures between the rear planet row pinion carrier rear planet row satellite gear identical with 4 structures, being set with No. two pads that other 4 structures are identical connects for contact, the two ends of rear planet row sun wheel endoporus are provided with No. three bearing shells and No. four bearing shells.
Output shaft described in technical scheme is ladder shaft type framing member, the shaft part of output shaft radius maximum is the shaft shoulder, the left side of the shaft shoulder is syllogic stepped shaft, is followed successively by from left to right first paragraph axle, second segment axle and the 3rd section of axle, and the radius of first paragraph axle, second segment axle and the 3rd section of axle increases successively; The right side of the shaft shoulder is two sectional type stepped shaft, is followed successively by from left to right optical axis section and splined shaft section, and the radius of optical axis section and splined shaft section reduces successively; On the rotation axis of output shaft, from left to right process a long blind hole, and the equipped part of and rear planet row sun wheel upper at output shaft (11) is radially processed the radial direction through hole that the long blind hole on 2～3 and axis communicates.
Compared with prior art the invention has the beneficial effects as follows:
1. the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention can realize electronic infinite variable speed function, ensures that engine operation, in best fuel-economy district, reduces oil consumption;
2. the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention can realize the pure electronic car pattern that opens, and eliminates the idling oil consumption of driving engine, improves car load fuel economy;
3. the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention can realize the recovery of the braking kinetic energy of vehicle, obviously improves the fuel economy of vehicle;
4. driving engine and the super capacitor in the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention can be exported energy simultaneously, improved the tractive performance of vehicle;
5. between the low-speed big pattern that the electric parallel-serial hybrid power system introducing of planetary bimodulus oil of the present invention bidirectional clutch can be turned round in simple stepless shift mode with to the further increasing of slowing down of front row output system, switch, make system under different operating conditions, obtain best combined efficiency;
6. the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention can reduce access times and the intensity of drg, extends its service life, reduces its maintenance, upkeep cost;
7. the driving engine that the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention can selection of small power meets the requirement of normally travelling of vehicle, reduces harmful gas emission, reduces the pollution to environment;
8. selecting under the condition of identical power source assembly, the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention can be exported larger drive torque with respect to existing hybrid power system, and better car load dynamic property is provided; Under the condition of the identical propulsive effort of output, the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention can be selected No. two motors that peak torque is less, has reduced the dependence of system to motor;
9. the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention is used super capacitor, can obtain larger horsepower output, and raising car load dynamic property also can more effective recovery braking energy, obviously improves car load fuel economy.
Brief description of the drawings
Below in conjunction with accompanying drawing, the present invention is further illustrated:
Fig. 1 is the schematic diagram of the electric parallel-serial hybrid power system architecture composition of planetary bimodulus oil of the present invention and principle of work;
Fig. 2 is the front view of front planet row structure composition in the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention;
Fig. 3 is that in the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention, front planet row removes the right elevation after gear ring cover;
Fig. 4 is the front view of rear planet row structure composition in the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention;
Fig. 5 is the front view of bidirectional clutch structure composition in the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention;
Fig. 6 is the front view of the electric parallel-serial hybrid power system architecture composition of planetary bimodulus oil of the present invention;
Fig. 7 is the whole performance map of driving engine in the electric parallel-serial hybrid power system of explanation planetary bimodulus oil of the present invention;
Fig. 8 is the whole performance map of a motor in the electric parallel-serial hybrid power system of explanation planetary bimodulus oil of the present invention;
Fig. 9 is the whole performance map of No. two motors in the electric parallel-serial hybrid power system of explanation planetary bimodulus oil of the present invention;
In figure: 1. driving engine, 2. a motor, 3. an inverter, 4. super capacitor, 5. front planet toothrow circle, 6. No. two inverters, 7. double-clutch, 8. No. two motors, 9. rear planet row gear ring, 10. rear planet row pinion carrier, 11. output shafts, 12 rear planet row sun wheels, 13. front planetary lines, 14. front planet row sun wheels, 15. engine output shafts, No. 16. pads, 17. front planet rows of planetary wheels, 18. front planet rows of planetary wheel bearing pins, No. 19. bearing pin sleeves, No. 20. bearing shells, 21. front planetary line left side rolling discs, 22. No. two bearing shells, 23. front planetary line left side rolling discs connect pawl, 24. No. two pads, 25. rear planet row satellite gears, 26. No. three bearing shells, 27. rear planet row satellite gear bearing pins, 28. No. two bearing pin sleeves, 29. rear planet row pinion carrier left side rolling discs, 30. No. four bearing shells, 31. casings, 32. left platens, 33. seal rings, 34. active friction plates, 35. driven friction disks, 36. right platens, 37. left clutch hubs, 38. right clutch hubs, 39. axle sleeves, A. a fuel feed hole, B. No. two fuel feed holes.
Detailed description of the invention
Below in conjunction with accompanying drawing, the present invention is explained in detail:
The object of this invention is to provide the electric parallel-serial hybrid power system of a kind of novel planetary formula bimodulus oil, a kind of oil electricity series-parallel hybrid electric system using double planet wheel rows of mixing as electric coupling apparatus is provided, to realize the electronic infinite variable speed function of series-parallel hybrid electric system, control engine is operated in best fuel-economy district, improve car load fuel economy, realize minimum discharge, overcome current parallel-serial hybrid power automobile large to motor dependence simultaneously, need large motor that the shortcoming of enough propulsive effort is provided, in addition, the planetary bimodulus electric parallel-serial hybrid power system of oil of the present invention adding due to power-transfer clutch, can realize the switching of two kinds of patterns, meet the different power demand of vehicle, to obtain higher comprehensive driving efficiency and fuel economy.
Consult Fig. 1 and Fig. 6, the electric parallel-serial hybrid power system of novel planetary formula bimodulus of the present invention oil is mainly made up of driving engine 1, motor 2, inverter 3, super capacitor 4, No. two inverters 6, double-clutch 7, No. two motors 8, output shaft 11, front planet row and rear planet rows.
Front planet row is sleeved on the right-hand member of engine output shaft 15 of driving engine 1 for being rotationally connected, the right-hand member of the front planet toothrow circle 5 in front planet row is sleeved on the first paragraph axle of output shaft 11 as being rotationally connected, double-clutch 7 is sleeved on the left end of output shaft 11, the left end of the left platen 32 in double-clutch 7 is that spline pair is connected with the right-hand member of front planet toothrow circle 5, No. two motors 8 are arranged on the output shaft 11 on double-clutch 7 right sides as being rotationally connected, rear planet row is arranged on the output shaft 11 on No. two motor 8 right sides, axle sleeve 39 right-hand members in double-clutch 7 are that spline pair is connected with the left end of the hollow shaft of No. two motors 8, the right-hand member of the hollow shaft of No. two motors 8 is that spline pair is connected with the left end of the rear planet row sun wheel 12 in rear planet row, motor 2 is sleeved on the engine output shaft 15 in front planet row left side as being rotationally connected, and the right-hand member of the hollow shaft of a motor 2 is that spline pair is connected with the left end of the front planet row sun wheel 14 in front planet row.
Consult Fig. 2, Fig. 3 and Fig. 6, front planet row of the present invention is mainly made up of the identical bearing pin sleeve of front planet toothrow circle 5, front planet row sun wheel 14,18,4 structures of front planet rows of planetary wheel bearing pin that 17,4 structures of front planet rows of planetary wheel that 16,4 structures of a pad that 13,8 structures of front planetary line are identical are identical are identical 19, bearing shell 20, front planetary line left side rolling disc 21 and No. two bearing shells 22.
Before 4 identical front planet rows of planetary wheels 17 of structure adopt respectively, planet rows of planetary wheel bearing pin 18 is arranged on front planetary line 13 and front planetary line left side rolling disc 21 equably, the front planet rows of planetary wheel stub end of bearing pin 18 and the counter sink of front planetary line 13 are interference fit, the rotation axis of the front planet rows of planetary wheel bearing pin 18 that 4 structures are identical is on the circumference apart from radiuses such as front planetary line 13 and front planetary line left side rolling disc 21 rotation axiss the rotation axis conllinear of front planetary line left side rolling disc 21 (front planetary line 13 with), 4 the identical front planet rows of planetary wheel rotation axis of bearing pin 18 and rotation axiss of front planetary line 13 of structure parallel, 4 identical identical front planet rows of planetary of 17 and 4 structures of front planet rows of planetary wheel of structure are taken turns between bearing pin 18 as being rotationally connected, in order to reduce friction between the two, between is provided with a bearing pin sleeve 19 for being rotationally connected, being arranged on the outside tooth of the front planet rows of planetary wheel 17 that 4 structures on front planetary line 13 are identical and the internal tooth of front planet toothrow circle 5 is meshed, the inner tines of the front planet rows of planetary wheel 17 that 4 structures are identical and the tooth of front planet row sun wheel 14 are meshed.The right-hand member of front planet toothrow circle 5 centre holes is connected with the left end of output shaft 11 by plain bearing, and the right-hand member of front planet toothrow circle 5 adopts spline pair to be connected with the left platen of double-clutch 32 left ends.Described front planetary line is an assembly set, it be made up of front planetary line 13 and front planetary line left side rolling disc 21 left and right two parts, and front planetary line left side rolling disc 21 is welded into one with front planetary line 13 by the pawl 23 that is connected of front planetary line left side rolling disc.Install additional in front planet rows of planetary wheel 17 and front planetary line 13 and front planet rows of planetary wheel 17 and the cooperation place of front planetary line left side rolling disc 21 16, numbers pads of a pad 16 with front planet row star-wheel bearing pin 18 for being rotationally connected.The described central through hole of front planetary line 13 and the large axle journal of the right-hand member place of engine output shaft 15 that the front planet rows of planetary wheel 17 that 4 structures are identical is installed is interference fit, front planet row sun wheel 14 is sleeved on the right-hand member of engine output shaft 15, and a bearing shell 20 and No. two bearing shells 22 are installed between the two ends of front planet row sun wheel 14 endoporus and engine output shaft 15.
Consult Fig. 1, Fig. 4 and Fig. 6, rear planet row of the present invention is mainly made up of rear planet row gear ring 9, rear planet row pinion carrier 10, rear planet row sun wheel 12, eight rear planet row satellite gears that 24,4 structures of No. two pads that structure is identical are identical 25, No. two bearing pin sleeves 28 that 27,4 structures of rear planet row satellite gear bearing pin that No. three 26,4 structures of bearing shell are identical are identical, rear planet row pinion carrier left side rolling disc 29, No. four bearing shells 30.
4 identical rear planet row satellite gear bearing pins 27 of structure are arranged on rear planet row pinion carrier 10 and rear planet row pinion carrier left side rolling disc 29, the stub end of rear planet row satellite gear bearing pin 27 and the counter sink of rear planet row pinion carrier 10 are interference fit, the rotation axis of the rear planet row satellite gear bearing pin 27 that 4 structures are identical is on the circumference apart from radiuses such as rear planet row pinion carrier 10 and rear planet row pinion carrier left side rolling disc 29 rotation axiss the rotation axis conllinear of rear planet row pinion carrier left side rolling disc 29 (the rear planet row pinion carrier 10 with), the rotation axis of the rear planet row satellite gear bearing pin 27 that 4 structures are identical and rear planet row pinion carrier 10 parallel with the rotation axis of rear planet row pinion carrier left side rolling disc 29,4 identical rear planet row satellite gears 25 of structure are sleeved on rear planet row satellite gear bearing pin 27, between the identical rear planet row satellite gear bearing pin 27 of 25 and 4 structures of rear planet row satellite gear that 4 structures are identical for being rotationally connected, in order to reduce friction between the two, between is provided with No. two bearing pin sleeves 28 for being rotationally connected, the identical outside tooth of rear planet row satellite gear 25 and the internal tooth of rear planet row gear ring 9 of 4 structures being arranged on rear planet row satellite gear bearing pin 27 is meshed, 4 the identical inner tines of rear planet row satellite gear 25 and teeth of rear planet row sun wheel 12 of structure are meshed.Rear planet row sun wheel 12 is sleeved on the right-hand member of output shaft 11, and the left end of rear planet row sun wheel 12 is connected with the right-hand member spline pair of the hollow shaft of No. two motors 8, and the castellated shaft of output shaft 11 right-hand members is that clutch end is connected with drive axle spline pair.Rear planet row gear ring 9 is connected on casing 31 by welding.Described rear planet row pinion carrier is an assembly set, it be made up of rear planet row pinion carrier 10 and rear planet row pinion carrier left side rolling disc 29 left and right two parts, and rear planet row pinion carrier left side rolling disc 29 is welded into one with rear planet row pinion carrier 10 by the pawl that is connected of rear planet row pinion carrier left side rolling disc.Install pad 24 at rear planet row satellite gear 25 and rear planet row pinion carrier 10 and rear planet row satellite gear 25 additional No. two with the cooperation place of rear planet row pinion carrier left side rolling disc 29.Rear planet row sun wheel 12 left ends and double-clutch right-hand member pass through spline joint.
Consult Fig. 5 and Fig. 6, double-clutch 7 of the present invention is for including the assembly set of left clutch and right clutch, mainly comprise casing 31, left platen 32, seal ring 33, the active friction plate 34 (left clutch is installed three with right clutch is each) that right platen 36,6 chip architectures are identical, the driven friction disk 35 (left clutch and right clutch are each installs three) that 6 chip architectures are identical, left clutch hub 37, right clutch hub 38, axle sleeve 39.
Described left platen 32 is arranged in casing 31 with right platen 36, between left platen 32 and right platen 36, be fixed together by screw, thereby guarantee to realize interlock from structure, the power of power-transfer clutch is from the left end input of left platen 32, and left clutch hub 37 and right clutch hub 38 are arranged in the annular chamber between left platen 32 and right platen 36.The alternate placement of driven friction disk 35 that active friction plate 34,6 chip architectures that 6 chip architectures are identical are identical is also divided into two groups, one group of active friction plate 34 and driven friction disk 35 are arranged in the annular chamber between left platen 32 and left clutch hub 37, and another group active friction plate 34 and driven friction disk 35 are arranged in the annular chamber between right clutch hub 38 and right platen 36.The active friction plate 34 that 6 chip architectures are identical coordinates with the female splines of opening at left platen 32 inner ring surface two ends by male splines, realizes power and passes to active friction plate 34 from left platen 32 with right platen 36.The driven friction disk 35 that 6 chip architectures are identical be arranged on left clutch hub 37 with on right clutch hub 38 for spline pair is connected, realize power and pass to left clutch hub 37 or right clutch hub 38 from active friction plate 34 and driven friction disk 35.The friction lining of double-clutch 7 is all to adopt multi-disc, active friction plate 34 and driven friction disk 35 are alternately, by moving axially of left platen 33 and right platen 36, compress active friction plate 34 and driven friction disk 35, between active friction plate 34 and driven friction disk 35, produce friction force, thereby make power pass to driven friction disk 35 from active friction plate 34.Left clutch arrives left clutch hub 37 by left platen 32, left clutch active friction plate 34, left clutch driven friction disk 35 by transmission of power successively, then is connected the Article 1 path of the output that realizes power with output shaft 11 by spline pair by left clutch hub 37; Right clutch successively by left platen 32, the right platen 36 that is connected by screw with left platen 32, right clutch active friction plate 34, right clutch driven friction disk 35 by transmission of power to right clutch hub 38, then by right clutch hub 38 by be connected with the axle sleeve 39 respectively Article 2 path of the output that realizes power of spline pair.
Described output shaft 11 is set to ladder shaft type framing member.Output shaft 11 radius the best parts are shaft shoulder structure, and the left side of the shaft shoulder is syllogic stepped shaft, are followed successively by from left to right first paragraph axle, second segment axle and the 3rd section of axle, and the radius of first paragraph axle, second segment axle and the 3rd section of axle increases successively; The right side of the shaft shoulder is two sectional type stepped shaft, is followed successively by from left to right optical axis section and splined shaft section, and the radius of optical axis section and splined shaft section reduces successively; Front planet toothrow circle 5 empty sets are on the first paragraph axle of output shaft 11.The axial location of front planet toothrow circle 5 on output shaft 11 positions by the left side of the second segment axle of output shaft 11.Second segment axle on output shaft 11 is connected with the left platen 32 in double-clutch by bearing shell, be that left platen 32 in double-clutch is contained on the second segment axle on output shaft 11 by axle bush sleeve, second segment axle on bearing shell and output shaft 11 is interference fit, and left platen 32 is free-running fit with bearing shell.Between left clutch hub 37 in the 3rd section of axle and power-transfer clutch 7 on output shaft 11, adopt spline pair to be connected.Left clutch hub 37 in power-transfer clutch 7 is axially all positioning by the shaft shoulder with right clutch hub 38.First the shaft shoulder right-hand member of output shaft 11 is connected with axle sleeve 39 by plain bearing, and axle sleeve 39 is sleeved on the optical axis on shaft shoulder right side of output shaft 11 by plain bearing.Axle sleeve left end is connected with the right clutch hub 38 in power-transfer clutch 7 by spline pair, and right-hand member is connected with the input shaft of No. two motors 8 by spline pair.In the rear planet row sun wheel 12 of right-hand member insertion in output shaft 11, for being rotationally connected, its right side and rear planet row pinion carrier 10 junctions are spline joint.For reducing right-hand member optical axis in output shaft 11 and the friction of rear planet row sun wheel 12 mating surfacess, between the two ends of rear planet row sun wheel 12 and the right-hand member optical axis of output shaft 11, install No. three bearing shells 26 and No. four bearing shells 30 additional.
No. two described motors 8 are sleeved on the stage casing optical axis of output shaft 11 as being rotationally connected, and the hollow shaft that output shaft 11 inserts No. two motors 8 is for being rotationally connected.The low order end of output shaft 11 connects car load drive axle, for outputing power.On the rotation axis of output shaft 11, from left to right process a long blind hole, and on output shaft 11, radially process with the equipped part of rear planet row sun wheel 12 radial direction through hole that the long blind hole on 2-3 and axis communicates, its effect is conveying lubricating oil.
Described driving engine 1, motor 2, No. two motors 8 and super capacitor 4 are all selected existing procucts, and concrete type selecting need, in conjunction with car load basic specification and designing requirement, describe in detail and consult table 1 and table 2.
Table 1 car load basic specification
Table 2 designing requirement
The main power source that described driving engine 1 is car load, its watt level need meet the dynamic property requirement of cruising with maximum speed on straight road surface, shown in (1):
In formula, P
efor the demand power of driving engine 1, V
afor speed of operation, η
tfor driving efficiency, M is the fully loaded quality of car load, and g is acceleration due to gravity, f
rfor the coefficient of rolling resistance of vehicle, ρ
afor density of air, C
dfor aerodynamic drag factor, the wind area that A is vehicle, i is the gradient.
Consult Fig. 7, in addition, the power of described driving engine 1 also requires to be greater than the average power of target circulation operating mode, to ensure electric quantity balancing in the process of moving, avoids super capacitor deep discharge.According to the designing requirement shown in the car load basic specification shown in table 1 and table 2, the principal parameter of selected engine product is as shown in table 3.The characteristic performance curve figure of this driving engine as shown in FIG..Meanwhile, according to the characteristic performance curve figure of driving engine 1, select engine operation in efficient district, 1100rpm is to 2200rpm.
Table 3 driving engine principal parameter
| Peak torque | 704Nm@1500rpm |
| Peak power | 147kw@2200rpm |
| Discharge capacity (ml) | 4980 |
| Idling (rpm) | 900 |
| Maximum speed of revolution (rpm) | 2500 |
Consult Fig. 8, a described motor 2 is for the rotating speed between decoupling zero driving engine 1 and wheel under different operating modes, make the rotating speed of driving engine 1 be independent of the rotating speed of wheel, coordinate No. two motors 8 to the torque decoupler between driving engine 1 and wheel, can ensure that driving engine 1 works in efficient district, to improve car load fuel economy.
First, for the rotation speed relation of a motor 2, requiring is zero in the speed of a motor vehicle, and the rotating speed of front planetary line 13 is 1 o'clock, the maximum functional rotating speed that the maximum speed of a motor 2 can balanced engine, shown in (2):
ω
MG1_max≥k
1ω
eexp (2)
In formula, ω
mG1_maxbe the maximum speed of a motor 2, ω
eexpfor the maximum functional rotating speed of driving engine 1, be 2200rpm, k
1for the characteristic parameter of front planet row, it is the ratio of the number of teeth of front planet toothrow circle 3 and the number of teeth of front planet row sun wheel 14.
Secondly, the torque of the torque of a motor 2 and driving engine 1 should meet the relation suc as formula (3), to ensure that motor 2 has the rotating speed of enough capacity adjusting driving engines 1.
T
emax≤k
1T
MG1_max (3)
In formula, T
emaxfor the maximum torque of driving engine 1, T
mG1_maxtorque while being motor 2 maximum speed.
The concrete numerical value of substitution, the principal parameter of a selected motor 2 is as shown in table 4, and its characteristic performance curve figure is as shown in Figure 8.
Motor principal parameter of table 4
| Motor type (interchange/PM) | PM |
| Motor rated power (kW) | 70 |
| Motor torque rating (Nm) | 334 |
| Motor peak power (kW) | 140 |
| Motor peak torque (Nm) | 668 |
| Maximum speed of revolution (rpm) | 4000 |
| Minimum steady speed (rpm) | 500 |
Consult Fig. 9, No. two described motors 8 require can provide peak power in limit accelerating mode, to ensure the tractive performance of car load.Accordingly, in limit accelerating mode, first calculate driving engine and overcome the surplus power of air resistance, rolling resistance and grade resistance horsepower, suc as formula (4),
Wherein: t
ifor driving engine opens time in machine moment, t
afor accelerating the time in end of a period moment, P
eMfor driving engine is delivered to the power of wheel, P by the mechanical path of EVT
rfor resistance power (equaling air resistance, rolling resistance sum grade resistance horsepower sum).
In addition, need calculate resistance due to acceleration power P
acc, shown in (5).Finally, the power of No. two motors 8 equals resistance due to acceleration power and deducts driving engine surplus power, shown in (6).
P
m＝P
acc-P
e,a (6)
In formula (5): δ is correction coefficient of rotating mass, v is the limiting condition speed of a motor vehicle in end of a period moment, is 50km/h.
Secondly, the maximum speed of revolution of No. two motors 8 also should meet the requirement of car load maximum speed, shown in (7).In formula, i
2for the fixed speed ratio that rear planet row forms, v
maxfor the maximum speed requiring, be 70km/h herein, r is vehicle wheel roll radius, i
dfor main reduction gear reduction ratio.
K
2for the characteristic parameter of front planet row, it is the ratio of the number of teeth of rear planet row gear ring 9 and the number of teeth of rear planet row sun wheel 12.
Finally, need calculate according to the speed of a motor vehicle of the normal operation of vehicle the base speed point of No. two motors 8, to ensure that No. two motors often work in the good region of efficiency.To sum up, the principal parameter that can obtain No. two motors 8 is as shown in table 5, and its characteristic performance curve figure as shown in Figure 9.
The principal parameter of No. two motors of table 5
| Motor type (interchange/PM) | PM |
| Motor rated power (kW) | 80 |
| Motor torque rating (Nm) | 311 |
| Motor peak power (kW) | 160 |
| Motor peak torque (Nm) | 622 |
| Maximum speed of revolution (rpm) | 7000 |
| Minimum steady speed (rpm) | 500 |
Described super capacitor 4 is aspect power, and requirement should have enough power to meet the requirement of vehicle power, and, in the pick-up time of specifying, the power sum of driving engine 1 and super capacitor 4 should be able to meet the overall power requirement of vehicle limiting condition.Aspect energy, require under limiting condition, in the pick-up time of specifying, the energy that super capacitor 4 can provide in the SOC discharge range allowing should meet whole full load accelerating mode to super capacitor energy requirement, be in accelerating mode, the energy of super capacitor 4 deducts the electric energy total amount that 2, motor can provide for No. two required gross energies of motor 8.According to requiring above, the principal parameter of super capacitor 4 of gained is as shown in table 6.
Table 6 super capacitor principal parameter
| Type | Carbon back super capacitor |
| Total internal resistance | 58.3mohm |
| Total volume | 20.27F |
| Total joint number | 148 |
| Voltage class | 400V，250V |
| Monomer parameter | 2.7V，3000F，0.394mohm |
Consult Fig. 1 and Fig. 6, described motor 2 empty sets are on engine output shaft 15, and engine output shaft 15 is through the hollow shaft of a motor 2.Before described engine output shaft 15 inserts, planet row sun wheel 14, for being rotationally connected, for reducing the friction drag of connecting surface, installs respectively a bearing shell 20 and No. two bearing shells 22 additional at the two ends of front planet row sun wheel 14.The right-hand member of engine output shaft 15 is processed as major diameter axle, with the centre hole of front planetary line 13 be interference fit.On the rotation axis of engine output shaft 15, process from right to left a long blind hole, and on engine output shaft 15, radially process with the equipped part of front planet row sun wheel 14 radial direction through hole that the long blind hole on 2-3 and axis communicates, its effect is conveying lubricating oil.
In addition, a described inverter 3 and No. two inverters 6 are selected according to the voltage class of a motor 2 and No. two motors 8 respectively.Three joints of a described motor 2 connect respectively three alternating current I/O joint x, y, z of inverter 3 by cable, the positive and negative connector of an inverter 3 and No. two inverters 6 adopts respectively cable to be connected with the both positive and negative polarity of super capacitor 4, and three joints of No. two motors 8 adopt cable to be connected with other three alternating current I/O joint x ', y ', the z ' of inverter 4 respectively.
The mode of operation of the electric parallel-serial hybrid power system of planetary bimodulus oil of the present invention is as shown in following table:
| Mode of operation | Energy source |
| Electric-only mode | Super capacitor 4 |
| Electronic infinite variable speed pattern | Driving engine 1 and super capacitor 4 |
| Regenerative brake pattern | Regenerating braking energy |
1. electric-only mode
Electric-only mode is mainly used in starting vehicle.Under this pattern, drive vehicle institute energy requirement all from super capacitor 4, be converted into mechanical energy by No. two motors 8, through after after the deceleration increasing torsion effect of planet row, output to car load drive axle.
2. electronic infinite variable speed pattern
Electronic infinite variable speed pattern can be divided into again driving engine 1 drive separately and combine drive two spermotypes.The common trait of this two spermotype is: now double-clutch 7 engages with rear planet row pinion carrier, a driving engine 1 horsepower output part is through front planet row, output to car load drive axle by mechanical path, another part is through front planet row, be converted into electric power by a motor 2, then be converted into mechanical horsepower by No. two motors 8 and output to car load drive axle.The difference of two spermotypes is: under the independent drive pattern of driving engine 1, whole power is from driving engine 1, and under associating drive pattern, part power is from super capacitor 4.
The division of two spermotypes is mainly according to the maximum output power of driving engine 1 Optimization Work curve.In the time that car load demand power is less than the maximum power of driving engine 1 Optimization Work curve, in the independent drive pattern of driving engine 1, all power is from driving engine 1, and control engine 1 works on Optimization Work curve, obtains good fuel economy; In the time that car load demand power is greater than the maximum power of driving engine 1 Optimization Work curve, driving engine 1 is operated on Optimal Curve maximum power point, and not enough car load demand power is supplied by super capacitor 4.
3. regenerative brake pattern
Regenerative brake pattern, according to the state of automobile, is divided into motor 8 braking and two kinds of situations of Associated brake No. two.
The in the situation that of non-emergent braking, and the speed of a motor vehicle is during higher than a certain limit value, enters regenerative brake pattern.If 8 maximum braking torques that can provide of No. two motors are provided demand braking torque now, just by No. two motor 8 independent brakes, the regenerating braking energy reclaiming is stored in super capacitor 4.If 8 maximum braking torques that can provide of No. two motors are provided the braking torque of demand, just by No. two motors 8 and mechanical brake Associated brake, part energy is reclaimed by No. two motors 8, is stored in super capacitor, and another part energy is dissipated with the form of heat energy by mechanical brake.
The principle features of the electric parallel-serial hybrid power system of planetary bimodulus oil:
1. according to the aperture of the position/throttle gate of the speed of a motor vehicle and acceleration pedal (also can consider demand power value), will be to ensure that driving engine 1 is operated in optimum efficiency region, ensure that in super capacitor 4, having certain energy of reserve (using while being acceleration or anxious acceleration) is prerequisite simultaneously, by adjusting the output torque of motor 2 rotating speeds and No. two motors 8, reasonable distribution demand torque between driving engine 1 and No. two motors 8.
2. the function of the motor 2 is here to adjust the rotating speed of driving engine 1 in best rotary speed area, the rotating speed phase decoupling zero of the rotating speed of driving engine 1 and wheel, but it should be noted that, due to the restriction of the maximum speed of revolution of a motor 2, can only the restriction to engine speed in the releasing speed of a motor vehicle to a certain degree.
No. two motors 8 have that high torque (HT) output characteristic can increase or supplementary car load drive axle on come from driving engine 1 torque to meet road surface torque-demand, the torque of driving engine 1 output decoupling zero from the demand torque of road surface out, has been removed to the restriction of the road surface demand torque causing because of mechanical connection between driving engine 1 and the axle drive shaft of car load to driving engine 1 torque.
4. the electric parallel-serial hybrid power system of this planetary bimodulus oil can obtain larger moment transmitting ratio, reduce the torque request of torque decoupler requirement to No. two motors 8, thereby can select peak torque less, No. two less motors 8 of size, are easier to be arranged in car load.
5. according to the height of the speed of a motor vehicle, select the left/right engagement state of double-clutch 7.In the time that double-clutch 7 engages with rear planet row sun wheel, the electric parallel-serial hybrid power system of this planetary bimodulus oil can realize front row output further to slow down to increase and turn round, and has ensured larger moment of torsion output, can be used for the operating mode of low-speed big, as climbing operating mode.
Therefore, ensureing under the prerequisite that car load requires in enough dynamic property, driving engine 1 can run on the fuel economy region of optimum efficiency, obtain higher fuel consumption and emission characteristic, and this planetary bimodulus parallel-serial hybrid power system can make car load reduce the demand of maximum engine torque or maximum power, thereby in the time of car load dynamic assembly parameter designing, reduce the dimensional characteristic to driving engine 1, make the Choice and design of driving engine 1 obtain larger degree of freedom, in addition, the mode of operation that adds the system of having enriched of double-clutch 7, can make system under different operating conditions, obtain best combined efficiency.
Claims (9)
1. the electric parallel-serial hybrid power system of planetary bimodulus oil, comprise driving engine (1), an inverter (3), super capacitor (4), No. two inverters (6), it is characterized in that, the described electric parallel-serial hybrid power system of planetary bimodulus oil also includes a motor (2), double-clutch (7), No. two motors (8), output shaft (11), front planet row and rear planet row;
Front planet row is sleeved on the right-hand member of engine output shaft (15) of driving engine (1) for being rotationally connected, the right-hand member of the front planet toothrow circle (5) in front planet row is sleeved on the first paragraph axle of output shaft (11) as being rotationally connected, double-clutch (7) is sleeved on the output shaft (11) on front planet row cover right side, the left end of the left platen (32) in double-clutch (7) is that spline pair is connected with the right-hand member of front planet toothrow circle (5), No. two motors (8) are arranged on the output shaft (11) on double-clutch (7) right side above for being rotationally connected, rear planet row is arranged on the output shaft (11) on No. two motors (8) right side, axle sleeve (39) right-hand member in double-clutch (7) is that spline pair is connected with the left end of the hollow shaft of No. two motors (8), the right-hand member of the hollow shaft of No. two motors (8) is that spline pair is connected with the left end of the rear planet row sun wheel (12) in rear planet row, a motor (2) is sleeved on the engine output shaft (15) in front planet row left side above for being rotationally connected, and the right-hand member of the hollow shaft of a motor (2) is that spline pair is connected with the left end of the front planet row sun wheel (14) in front planet row.
2. according to the electric parallel-serial hybrid power system of planetary bimodulus oil claimed in claim 1, it is characterized in that, three joints of a described motor (2) connect respectively three alternating current I/O joint x of an inverter (3) by cable, y, z, three joints of No. two motors (8) adopt cables respectively with three alternating current I/O joint x ' of No. two inverters (6), y ', z ' connects, an inverter (3) adopts respectively cable to be connected with the both positive and negative polarity of super capacitor (4) with the positive and negative connector of No. two inverters (6).
3. according to the electric parallel-serial hybrid power system of planetary bimodulus oil claimed in claim 1, it is characterized in that, described double-clutch (7) also comprises casing (31), right platen (36), the active friction plate (34) that 6 chip architectures are identical, driven friction disk (35), left clutch hub (37), the right clutch hub (38) and axle sleeve (39) that 6 chip architectures are identical;
Described left platen (32) is arranged in casing (31) with right platen (36), between left platen (32) and right platen (36), be fixed together by screw, left clutch hub (37) and right clutch hub (38) are arranged in the annular chamber between left platen (32) and right platen (36), active friction plate (34) that 6 chip architectures the are identical driven friction disk (35) identical with 6 chip architectures alternately and be divided into two groups, one group of active friction plate (34) and driven friction disk (35) are arranged in the annular chamber between left platen (32) and left clutch hub (37), another group active friction plate (34) and driven friction disk (35) are arranged in the annular chamber between right clutch hub (38) and right platen (36), the active friction plate (34) that 6 chip architectures are identical adopts spline pair to be connected with the two ends of left platen (32) inner ring surface, the driven friction disk (35) that 6 chip architectures are identical adopts spline pair to be connected with left clutch hub (37) with the outer ring surface of the ring shaped axial boss of right clutch hub (38), left clutch hub (37) is connected with axle sleeve (39) with output shaft (11) by spline pair successively with right clutch hub (38).
4. according to the electric parallel-serial hybrid power system of planetary bimodulus oil described in claim 1 or 3, it is characterized in that, described axle sleeve (39) is sleeved on the optical axis on output shaft (11) shaft shoulder right side, between the optical axis on the two ends of axle sleeve (39) and output shaft (11) shaft shoulder right side, plain bearing is installed, the right side of the left side of axle sleeve (39) and output shaft (11) shaft shoulder is sliding block joint, left platen (32) is sleeved on the second segment axle of output shaft (11), between the second segment axle of left platen (32) and output shaft (11), bearing shell is installed, the second segment axle of bearing shell and output shaft (11) is interference fit, between left platen (32) and bearing shell, it is free-running fit, on the external cylindrical surface that left platen (32) contacts with casing (31) inner ring surface, be provided with seal groove, seal ring (33) is installed in seal groove.
5. according to the electric parallel-serial hybrid power system of planetary bimodulus oil claimed in claim 1, it is characterized in that, described front planet row also comprises front planetary line (13), 4 front planet rows of planetary wheel (17), 4 front planet rows of planetary wheel bearing pins (18) and front planetary line left side rolling disc (21) that structure is identical that structure is identical;
4 identical front planet rows of planetary wheel bearing pins (18) of structure are arranged on front planetary line (13) and front planetary line left side rolling disc (21), the rotation axis of the front planet rows of planetary wheel bearing pin (18) that 4 structures are identical is on the circumference of the radiuses such as the rotation axis apart from front planetary line (13) and front planetary line left side rolling disc (21), 4 identical front planet rows of planetary wheels (17) of structure are sleeved on 4 identical front planet rows of planetary of structure and take turns bearing pin (18) above for being rotationally connected, outside tooth and the front planet toothrow circle (5) of the front planet rows of planetary wheel (17) that 4 structures are identical are connected with a joggle, inner tines and the front planet row sun wheel (14) of the front planet rows of planetary wheel (17) that 4 structures are identical are connected with a joggle.
6. according to the electric parallel-serial hybrid power system of planetary bimodulus oil claimed in claim 5, it is characterized in that, the front planet rows of planetary that the identical front planet rows of planetary wheel (17) of 4 described structures is identical with 4 structures is taken turns between bearing pin (18) 4 bearing pin sleeves (19) that structure is identical is installed, on the identical front planet rows of planetary wheel bearing pin (18) of 4 structures between front planetary line left side rolling disc (21) the front planet rows of planetary wheel (17) identical with 4 structures, being set with 4 identical pads (16) of structure is contact connection, on the identical front planet rows of planetary wheel bearing pin (18) of 4 structures between front planetary line (13) the front planet rows of planetary wheel (17) identical with 4 structures, being set with a pad (16) that other 4 structures are identical connects for contact, the two ends of front planet row sun wheel (14) endoporus are provided with a bearing shell (20) and No. two bearing shells (22).
7. according to the electric parallel-serial hybrid power system of planetary bimodulus oil claimed in claim 1, it is characterized in that, described rear planet row also comprises rear planet row gear ring (9), rear planet row pinion carrier (10), 4 rear planet row satellite gear (25), 4 rear planet row satellite gear bearing pins (27) and rear planet row pinion carrier left side rolling disc (29) that structure is identical that structure is identical;
4 identical rear planet row satellite gear bearing pins (27) of structure are arranged on rear planet row pinion carrier (10) and rear planet row pinion carrier left side rolling disc (29), the rotation axis of the rear planet row satellite gear bearing pin (27) that 4 structures are identical is on the circumference apart from radiuses such as rear planet row pinion carrier (10) and rear planet row pinion carrier left side rolling disc (29) rotation axiss, 4 identical rear planet row satellite gears (25) of structure are sleeved on 4 identical rear planet row satellite gear bearing pins (27) of structure and go up as being rotationally connected, outside tooth and the rear planet row gear ring (9) of the rear planet row satellite gear (25) that 4 structures are identical are connected with a joggle, inner tines and the rear planet row sun wheel (12) of the rear planet row satellite gear (25) that 4 structures are identical are connected with a joggle.
8. according to the electric parallel-serial hybrid power system of planetary bimodulus oil claimed in claim 7, it is characterized in that, between the identical rear planet row satellite gear bearing pin (27) of the rear planet row satellite gear (25) that 4 described structures are identical and 4 structures, 4 No. two bearing pin sleeves (28) that structure is identical are installed, on the identical rear planet row satellite gear bearing pin (27) of 4 structures between rear planet row pinion carrier left side rolling disc (29) the rear planet row satellite gear (25) identical with 4 structures, being set with 4 identical No. two pads (24) of structure is contact connection, on the identical rear planet row satellite gear bearing pin (27) of 4 structures between rear planet row pinion carrier (10) the rear planet row satellite gear (25) identical with 4 structures, being set with No. two pads (24) that other 4 structures are identical connects for contact, the two ends of rear planet row sun wheel (12) endoporus are provided with No. three bearing shells (26) and No. four bearing shells (30).
9. according to the electric parallel-serial hybrid power system of planetary bimodulus oil claimed in claim 1, it is characterized in that, described output shaft (11) is ladder shaft type framing member, the shaft part of output shaft (11) radius maximum is the shaft shoulder, the left side of the shaft shoulder is syllogic stepped shaft, be followed successively by from left to right first paragraph axle, second segment axle and the 3rd section of axle, the radius of first paragraph axle, second segment axle and the 3rd section of axle increases successively; The right side of the shaft shoulder is two sectional type stepped shaft, is followed successively by from left to right optical axis section and splined shaft section, and the radius of optical axis section and splined shaft section reduces successively; On the rotation axis of output shaft (11), from left to right process a long blind hole, and the equipped part of and rear planet row sun wheel (12) upper at output shaft (11) is radially processed the radial direction through hole that the long blind hole on 2～3 and axis communicates.
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