CN203449917U - Planetary dual-mode oil-electricity series-parallel hybrid power system - Google Patents

Abstract

The utility model discloses a planetary dual-mode oil-electricity series-parallel hybrid power system, which can solve the problems that an existing series-parallel hybrid power automobile greatly depends on a motor, and a current planetary series-parallel hybrid power automobile can not fully realize a parallel connection mode and can not sufficiently optimize transmission efficiency. The system comprises an engine, a No. 1 motor, an inverter, a supercapacitor, a No. 2 motor, a front planet row, a rear planet row, a clutch, a system output shaft and a system input shaft, wherein the engine is connected with the system input shaft through a shaft coupling, the front planet row is sheathed at the right end of the system input shaft, the No. 1 motor is idly sheathed at the left end of the system input shaft, the right end of the No. 1 motor is in spline connection with the left end of the front planet row, the clutch is in spline connection with the front planet row, the front planet row is in spline connection with the system output shaft, the rear planet row is sheathed on the system output shaft, the No. 2 motor is idly sheathed at the right end of the system output shaft, and the left end of the No. 2 motor is in spline connection with the right end of the rear planet row.

Description

The electric parallel-serial hybrid power system of planetary bimodulus oil

Technical field

The utility model relates to a kind of power system of hybrid vehicle, and or rather, the utility model relates to the electric parallel-serial hybrid power system of a kind of planetary bimodulus oil.

Background technology

In the face of energy shortage and the day by day serious present situation of environmental pollution, energy-saving and environmental protection become the only way of development of automobile.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 guarantee that driving engine is all the time in work area preferably; And series-parallel connection can be evaded the shortcoming of the two in conjunction with the advantage of series and parallel connections, it is the configuration scheme of optimizing the most.

Current Series-Parallel HEV mainly adopts planetary mechanism as power dividing device, and typical version comprises the THS system (Toyota's hybrid power system) of Toyota and general AHS system (senior hybrid power 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 when 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, so its driving efficiency in high velocity is less.The AHS system of General Corporation adopts double Huo San rows of planetary mechanism 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, yet the control that often needs a plurality of power-transfer clutchs in AHS system comes implementation pattern to switch, and this makes the structure of whole system very complicated, control difficulty and also increased a lot.

Summary of the invention

Technical problem to be solved in the utility model is that to have overcome current parallel-serial hybrid power automobile large to motor dependence, need large motor that the problem of enough propulsive effort is provided, and current planetary parallel-serial hybrid power automobile can not realize the problem that paralleling model so that driving efficiency are optimized not completely, provide a kind of planetary bimodulus oil electric parallel-serial hybrid power system.

For solving the problems of the technologies described above, the utility model is to adopt following technical scheme to realize, by reference to the accompanying drawings: the described electric parallel-serial hybrid power system of planetary bimodulus oil comprises driving engine 1, a motor 2, inverter 4, super capacitor 5, No. two motors 7, front planet row and rear planet row, wherein, front planet toothrow circle 11 is drawn together in front planet package, 4 front planet rows of planetary wheels 16 that structure is identical, front planet row sun wheel 13, front planetary line 12, a sleeve 19, No. two sleeves 23, adjust pad 22 No. one, front planetary line left side 21, front planet toothrow snare 20, 4 bearing pin sleeves 18 that structure is identical, 4 front planet rows of planetary wheel bearing pins 17 and 8 pads 15 that structure is identical that structure is identical, rear planet row comprises No. two bearing pin sleeves that the rear planet row satellite gear 26 that 6,4 structures of rear planet row gear ring are identical, rear planet row sun wheel 9, rear planet row pinion carrier 10,29,4, rear planet row pinion carrier right side structure are identical 28, eight identical rear planet row satellite gear bearing pins 27 of 25,4 structures of No. two pads that structure is identical, No. one motor 2 is spline joint with front planet row sun wheel 13, and No. two motor 7 is spline joint with rear planet row sun wheel 9, and No. one motor 2 is connected with inverter 4 by cable respectively with No. two motors 7, and inverter 4 is connected with super capacitor 5 by cable, this system also comprises power-transfer clutch 3, system output shaft 8, system input shaft 14, wherein, driving engine 1 is connected with system input shaft 14 by coupler, motor 2 empty set are at the left end of system input shaft 14, front planet row is sleeved on the right-hand member of system input shaft 14, the right-hand member of a motor 2 is that spline pair is connected with the left end of front planet row sun wheel 13 in front planet row, before power-transfer clutch 3 is sleeved in front planet row, the left end of planet row sun wheel 13 is that spline pair connects, the right-hand member of front planet row is that spline pair is connected with the left end of system output shaft 8, rear planet row is sleeved on the left end of system output shaft 8, No. two motor 7 empty sets are at the right-hand member of system output shaft 8, the left end of No. two motors 7 is that spline pair is connected with the right-hand member of rear planet row.

According to the utility model, provide a kind of planetary bimodulus oil electric parallel-serial hybrid power system, wherein, the rotation axis conllinear of system input shaft 14, motor 2, power-transfer clutch 3, front planet row, rear planet row, No. two motors 7, system output shaft 8.

According to the utility model, provide a kind of planetary bimodulus oil electric parallel-serial hybrid power system, wherein, power-transfer clutch 3 includes casing 32, annular piston 33, seal ring 34, three friction linings that structure is identical 35, three steel discs that structure is identical 36, platen 37, snap ring 38, clutch hub 39, spring pedestal 40, four springs that structure is identical 41 and lesser calorie ring 42; clutch hub 39 is that spline pair is connected with the middle part of front planet row sun wheel 9 in front planet row, the face of cylinder, outside of clutch hub 39 centre holes and three steel disc 36 spline pairs connections that structure is identical, spring pedestal 40 is sleeved on the face of cylinder, outside of clutch hub 39 centre holes as being rotationally connected, four identical springs 41 of structure are put into four grooves on spring pedestal 40 successively, it is sliding block joint that annular piston 33 is sleeved on the face of cylinder, outside of casing 32 centre holes, on the left circles ring wall being connected with casing 32 center hole walls, an oil inlet A is set, between the friction lining 35 identical with three structures of the face of cylinder, inner side of casing 32, be that spline pair connects, the steel disc 36 that the identical friction lining 35 of three structures is identical with three structures is alternate installation, between the friction lining 35 that three structures the are identical under normal conditions steel disc 36 identical with three structures, it is free-running fit, right side at the identical friction lining 35 of three structures of the alternate installation steel disc 36 identical with three structures is provided with platen 37.

According to the utility model, provide a kind of planetary bimodulus oil electric parallel-serial hybrid power system, wherein, clutch hub 39 is a ring-type element, the centre hole of clutch hub 39 is processed with female splines, for being connected with the stage casing castellated shaft of front planet row sun wheel 13, on the outside disc of clutch hub 39, be processed with equally spaced three splines, three splines coordinate with the female splines of three steel discs 36 respectively; On the face of cylinder, outside of clutch hub 39 centre holes, be processed with an annular groove, lesser calorie ring 42 packs in annular groove, and is connected with spring pedestal 40 right side contacts; On spring pedestal 40, be evenly distributed with four uniform grooves, be respectively used to place four springs 41; On the disc of the outside of annular piston, be processed with a groove, and install seal ring 34 additional; On the inner headed face of casing 32, process three equidistant splines, coordinate with the male splines of three friction linings 35 respectively.

According to the utility model, provide a kind of planetary bimodulus oil electric parallel-serial hybrid power system, wherein, system output shaft 8 is stepped shaft, the right-hand member centre hole spline joint of the left end of system output shaft 8 and front planet toothrow snare 20; System output shaft 8 is processed with flange segments at the left end of rear planet row sun wheel 9, and the centre hole of flange segments and rear planet row pinion carrier 10 is interference fit; System output shaft 8 passes rear planet row sun wheel 9 and is rotationally connected with rear planet row sun wheel 9; No. two motor 7 empty sets are in the stage casing of system output shaft 8, and system output shaft 8 is rotationally connected through 7 hollow realization of No. two motors; The right-hand member of system output shaft 8 connects car load drive axle.

According to the utility model, provide a kind of planetary bimodulus oil electric parallel-serial hybrid power system, wherein, No. one motor 2 is spline joint with front planet row sun wheel 13, system input shaft 14 is through the hollow and front planetary line interference fit of front planet row sun wheel 13, the left end of the right-hand member of front planet toothrow circle 11 and front planet toothrow snare 20 is spline joint, and the right-hand member of front planet toothrow snare 20 centre holes adopts spline pair to be connected with the left end of system output shaft 8; Front planetary line is an assembly set, and it is comprised of front planetary line 12 and front planetary line left side 21, and front planetary line left side 21 is welded into one with front planetary line 12 by the pawl 43 that is connected on the left of front planetary line.4 identical front planet rows of planetary wheels 16 of structure are evenly distributed on front planetary line 12 by front planet rows of planetary wheel bearing pin 17 respectively, be arranged on the outside tooth of the front planet rows of planetary wheel 16 that 4 structures on front planetary line 12 are identical and the internal tooth of front planet toothrow circle 11 and be meshed, the inner tines of the front planet rows of planetary wheel 16 that 4 structures are identical and the tooth of front planet row sun wheel 13 are meshed.

According to the utility model, provide a kind of planetary bimodulus oil electric parallel-serial hybrid power system, wherein, rear planet row also comprises No. three sleeves 24, No. four sleeves 31 and adjusts pads 30 No. two, No. three sleeves 24 and No. four sleeves 31 are arranged on respectively the two ends of rear planet row sun wheel 9, adjusting pad 30 No. two is connected with rear planet row pinion carrier right side 29 bolts, the centre hole of No. two adjustment pads 30 and rear planet row sun wheel 9 are for being rotationally connected, and rear planet row sun wheel 9 and No. two motors 7 are spline joint.

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

1. the electric parallel-serial hybrid power system of planetary bimodulus oil described in the utility model, compares the planetary hybrid power system of existing single mode, can realize paralleling model, can obtain better comprehensive driving efficiency and car load fuel economy.

2. the electric parallel-serial hybrid power system of planetary bimodulus oil described in the utility model, with respect to existing hybrid power system, simple in structure, compact, required installing space is less, only has a power-transfer clutch, is easy to control.

3. the electric parallel-serial hybrid power system of planetary bimodulus oil described in the utility model can realize electronic infinite variable speed function, guarantees that engine operation, in best fuel-economy district, reduces oil consumption.

4. the electric parallel-serial hybrid power system of planetary bimodulus oil described in the utility model can realize the pure electronic car pattern that opens, and eliminates the idling oil consumption of driving engine, improves car load fuel economy.

5. the electric parallel-serial hybrid power system of planetary bimodulus oil described in the utility model can realize the recovery of vehicle braking kinetic-energy, obviously improves the fuel economy of vehicle.

6. driving engine and the super capacitor in the electric parallel-serial hybrid power system of planetary bimodulus oil described in the utility model can be exported energy simultaneously, improved the tractive performance of vehicle.

7. the electric parallel-serial hybrid power system of planetary bimodulus oil described in the utility model can reduce access times and the intensity of drg, extends its service life, reduces its maintenance, upkeep cost.

8. the driving engine that the electric parallel-serial hybrid power system of planetary bimodulus oil described in the utility model can selection of small power meets the requirement of normally travelling of vehicle, reduces harmful gas emission, reduces the pollution to environment.

9. selecting under the condition of identical power source assembly, the electric parallel-serial hybrid power system of planetary bimodulus oil described in the utility model, with respect to existing hybrid power system, can export larger drive torque, 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 described in the utility model can be selected No. two motors that peak torque is less, has reduced the dependence of system to motor.

10. the electric parallel-serial hybrid power system of planetary bimodulus oil described in the utility model 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.

Accompanying drawing explanation

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

Fig. 1 is the schematic diagram of the explanation electric parallel-serial hybrid power system architecture composition of planetary bimodulus oil described in the utility model and principle of work;

Fig. 2 is the front view that in the electric parallel-serial hybrid power system of explanation planetary bimodulus oil described in the utility model, front planet row structure forms;

Fig. 3 is that in the electric parallel-serial hybrid power system of explanation planetary bimodulus oil described in the utility model, front planet row removes the right elevation after gear ring cover;

Fig. 4 is the front view that in the electric parallel-serial hybrid power system of explanation planetary bimodulus oil described in the utility model, rear planet row structure forms;

Fig. 5 is the front view that the structure of power-transfer clutch in the electric parallel-serial hybrid power system of explanation planetary bimodulus oil described in the utility model forms;

Fig. 6 is the front view that the structure of the electric parallel-serial hybrid power system of explanation planetary bimodulus oil described in the utility model forms;

Fig. 7 is the whole performance map of driving engine in the electric parallel-serial hybrid power system of explanation planetary bimodulus oil described in the utility model;

Fig. 8 is the whole performance map of a motor in the electric parallel-serial hybrid power system of explanation planetary bimodulus oil described in the utility model;

Fig. 9 is the whole performance map of No. two motors in the electric parallel-serial hybrid power system of explanation planetary bimodulus oil described in the utility model;

In figure: 1. driving engine, 2. a motor, 3. power-transfer clutch, 4. inverter, 5. super capacitor, 6. rear planet row gear ring, 7. No. two motors, 8. system output shaft, 9. rear planet row sun wheel, 10. rear planet row pinion carrier, 11. front planet toothrow circles, 12. front planetary lines, 13. front planet row sun wheels, 14. system input shafts, No. 15. pads, 16. front planet rows of planetary wheels, 17. front planet rows of planetary wheel bearing pins, No. 18. bearing pin sleeves, No. 19. sleeves, 20. front planet toothrow snares, 21. front planetary line left sides, adjust pad 22. No. one, 23. No. two sleeves, 24. No. three sleeves, 25. No. two pads, 26. rear planet row satellite gears, 27. rear planet row satellite gear bearing pins, 28. No. two bearing pin sleeves, 29. rear planet row pinion carrier right sides, adjust pad 30. No. two, 31. No. four sleeves, 32. casings, 33. annular pistons, 34. seal rings, 35. friction linings, 36. steel discs, 37. platens, 38. snap rings, 39. clutch hubs, 40. spring perches, 41. springs, 42. little snap rings, 43. front planetary line left sides connect pawl, A. fuel feed hole.

The specific embodiment

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

The purpose of this utility model is to provide a kind of new oil electricity series-parallel hybrid electric system, a kind of oil electricity series-parallel hybrid electric system of double planet wheel rows of mixing as electric coupling apparatus of usining be 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 described in the utility model adding due to power-transfer clutch, can realize paralleling model completely, obtain comprehensive driving efficiency and the car load fuel economy more optimized.

Consult Fig. 1 and Fig. 6, the electric parallel-serial hybrid power system of planetary bimodulus oil described in the utility model is mainly comprised of driving engine 1, motor 2, power-transfer clutch 3, inverter 4, super capacitor 5, No. two motors 7, system output shaft 8, system input shaft 14, front planet row and rear planet rows.Driving engine 1 is connected with system input shaft 14 by coupler, No. one motor 2 is sleeved on the left end of system input shaft 14, the right-hand member of a motor 2 is that spline pair is connected with the left end of front planet row sun wheel 13, power-transfer clutch 3 is that spline pair is connected by clutch hub 39 and the middle part of front planet row sun wheel 13, front planet row is sleeved on the right-hand member of system input shaft 14, system input shaft 14 packs in the centre hole of front planet row sun wheel 13, the right-hand member flange segments of system input shaft 14 and the centre hole of front planetary line 12 are interference fit, front planet row is that spline pair is connected by the right-hand member of front planet toothrow snare 20 and the left end of system output shaft 8, rear planet row is sleeved on the left end of system output shaft 8, the left end flange segments of system output shaft 8 and rear planet row pinion carrier 10 are interference fit, No. two motor 7 empty sets are at the right-hand member of system output shaft 8, the left end of No. two motors 7 is that spline pair is connected with the right-hand member of rear planet row sun wheel 9.In addition, No. one motor 2 is connected with inverter 4 by cable respectively with No. two motors 7, and inverter 4 is connected with super capacitor 5 by cable.The rotation axis conllinear of system input shaft 14, motor 2, power-transfer clutch 3, front planet row, rear planet row, No. two motors 7, system output shaft 8.

Consult Fig. 2, Fig. 3 and Fig. 6, the front planet row that the utility model adopts mainly by the identical front planet rows of planetary wheel 16 of 11,4 structures of front planet toothrow circle, front planet row sun wheel 13, front planetary line 12, sleeve 19, No. two sleeves 23, adjust the pad 15 that front planet rows of planetary wheel bearing pin 17 that pad 22, front planetary line left side 21,18,4 structures of a bearing pin sleeve that 20,4 structures of front planet toothrow snare are identical are identical is identical with 8 structures for No. one and form.

4 identical front planet rows of planetary wheels 16 of structure are evenly distributed on front planetary line 12 by front planet rows of planetary wheel bearing pin 17 respectively, the front planet rows of planetary wheel stub end of bearing pin 17 and the counter sink of front planetary line 12 are interference fit, the rotation axis of the front planet rows of planetary wheel 16 that 4 structures are identical is positioned on the circumference of the radiuses such as front planetary line 12 rotation axiss, the rotation axis of the front planet rows of planetary wheel 16 that 4 structures are identical and the rotation axis of front planetary line 12 parallel, the front planet rows of planetary that the identical front planet rows of planetary wheel 16 of 4 structures is identical with 4 structures is taken turns between bearing pin 17 as being rotationally connected, in order to reduce friction between the two, between is provided with a bearing pin sleeve 18 for being rotationally connected, being arranged on the outside tooth of the front planet rows of planetary wheel 16 that 4 structures on front planetary line 12 are identical and the internal tooth of front planet toothrow circle 11 is meshed, the inner tines of the front planet rows of planetary wheel 16 that 4 structures are identical and the tooth of front planet row sun wheel 13 are meshed.The right-hand member of front planet toothrow circle 11 is that spline pair is connected with the left end of front planet toothrow snare 20, and the right-hand member of front planet toothrow snare 20 centre holes adopts spline pair to be connected with the left end of system output shaft 8.Front planetary line 12 forms an assembly set with front planetary line left side 21, and front planetary line left side 21 is welded into one with front planetary line 12 by the pawl 43 that is connected on the left of front planetary line.For the ease of adjusting the axial location of front planet row, on front planetary line left side 21, install additional and adjust pad 22 for No. one for bolt connection, the left end that the centre hole of an adjustment pad 22 is sleeved on front planet row sun wheel 13 is that noncontact connects.On the front planet row star-wheel bearing pin 17 of front planet rows of planetary wheel 16 and front planetary line 12 and front planet rows of planetary wheel 16 and the cooperation place in front planetary line left side 21, being set with 15, numbers pads 15 of a pad, to take turns between bearing pin 17 with front planet rows of planetary be free-running fit.The described central through hole of front planetary line 12 and the right-hand member flange segments of system input shaft 14 that the front planet rows of planetary wheel 16 that 4 structures are identical is installed is interference fit.

Consult Fig. 1, Fig. 4 and Fig. 6, the rear planet row that the utility model adopts mainly by identical No. two bearing pin sleeves of the identical rear planet row satellite gear 26 of 6,4 structures of rear planet row gear ring, rear planet row sun wheel 9, rear planet row pinion carrier 10,29,4, rear planet row pinion carrier right side structure 28, eight rear planet row satellite gear bearing pins that 25,4 structures of No. two pads that structure is identical are identical 27, No. three sleeves 24, adjust pad 30 for No. two, No. four sleeves 31 form.

4 identical rear planet row satellite gears 26 of structure are evenly distributed in rear planet row pinion carrier 10 by rear planet row satellite gear bearing pin 27 respectively, the stub end of rear planet row satellite gear bearing pin 27 and the counter sink of rear planet row pinion carrier 9 are interference fit, the rotation axis of the rear planet row satellite gear 26 that 4 structures are identical is on the circumference of the radiuses such as rotation axis apart from rear planet row pinion carrier 9,4 the identical rotation axis of rear planet row satellite gear 26 and rotation axiss of rear planet row pinion carrier 10 of structure parallel, between the identical rear planet row satellite gear 26 of 4 structures rear planet row satellite gear bearing pin 27 identical with 4 structures 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 26 and the internal tooth of rear planet row gear ring 6 of 4 structures being arranged in rear planet row pinion carrier 10 is meshed, 4 the identical inner tines of rear planet row satellite gear 26 and teeth of rear planet row sun wheel 9 of structure are meshed.The right-hand member of rear planet row sun wheel 9 is that spline pair is connected with the mouth of No. two motors 7.Rear planet row gear ring 6 is connected on casing 32 by welding, and housing 32 is for holding whole system.Rear planet row pinion carrier 10 forms an assembly set with rear planet row pinion carrier right side 29, and rear planet row pinion carrier right side 29 is welded into one with rear planet row pinion carrier 10 by the pawl that is connected on rear planet row pinion carrier right side 29.For the ease of adjusting the axial location of rear planet row, on rear planet row pinion carrier right side 29, install No. two additional and adjust pad 30, rear planet row pinion carrier right side 29 with adjust pad 30 for No. two and be connected for bolt, adjust pad 30 empty sets for No. two in rear planet row sun wheel 9, and the centre hole of adjusting pad 30 for No. two is coaxial with rear planet row sun wheel 9, on the rear planet row satellite gear bearing pin 27 between rear planet row satellite gear 26 and rear planet row pinion carrier 10 and rear planet row satellite gear 26 and rear planet row pinion carrier right side 29, install pad 25 additional No. two, between No. two pads 25 and rear planet row satellite gear bearing pin 27 for being rotationally connected.The left end macro-axis cervical part of esophagus of the left end endoporus of rear planet row pinion carrier 10 and system output shaft 8 is interference fit.

Described system output shaft 8 is set to stepped shaft.The left end of system output shaft 8 is that spline pair is connected with the right-hand member centre hole of front planet toothrow snare 20.System output shaft 8 is processed a major diameter shaft part at the left end of rear planet row sun wheel 9, i.e. flange segments, and the centre hole of flange segments and rear planet row pinion carrier 10 is interference fit.After system output shaft 8 inserts, the centre hole of planet row sun wheel 9 is interior for being rotationally connected, and for reducing the friction of mating surfaces, installs respectively No. three sleeves 24 and No. four sleeves 31 at the two ends of rear planet row sun wheel 9 additional.No. two described motor 7 empty sets are in the stage casing of system output shaft 8, i.e. the centre hole of No. two motors 7 of system output shaft 8 insertions is interior for being rotationally connected.The right-hand member of system output shaft 8 connects car load drive axle, for outputing power.On the rotation axis of system output shaft 8, from left to right process a long blind hole, and on system output shaft 8, radially process with the equipped part of rear planet row sun wheel 9 radial direction through hole that the long blind hole on 2-3 and axis communicates, its effect is conveying lubricating oil.

Consult Fig. 5 and Fig. 6, power-transfer clutch 3 described in the utility model is an assembly set, mainly comprises casing 32, annular piston 33, seal ring 34, three friction linings that structure is identical 35, three steel discs that structure is identical 36, platen 37, snap ring 38, clutch hub 39, spring pedestal 40, four springs that structure is identical 41, lesser calorie ring 42.

Described clutch hub 39 is a ring-type element, and its centre hole is processed with female splines, for the castellated shaft of the stage casing hollow with front planet row sun wheel 13, is connected.On the face of cylinder, outside of clutch hub 39, be processed with equally spaced three splines, the female splines of the steel disc 36 identical with three structures coordinates respectively.Described spring pedestal 40 is also a ring-type element, spring pedestal 40 is sleeved on the face of cylinder, outside of clutch hub 39 centre holes, the face of cylinder, outside of its centre hole and clutch hub 39 centre holes is for being rotationally connected, position for restraining spring base 40, on the face of cylinder, outside of clutch hub 39 centre holes, process an annular groove, packed lesser calorie ring 42 into.On spring pedestal 40, processed four uniform grooves, four identical springs 41 of structure are put into groove successively.It is sliding block joint that the centre hole of described annular piston 33 is sleeved on the face of cylinder, outside of casing 32 centre holes, casing 32 is sleeved on the face of cylinder, outside of clutch hub 39 centre holes as being rotationally connected, the circular groove on the left side of annular piston 33 and casing 32 right sides forms annular hydraulic fluid cylinder, on the left circles ring wall being connected with casing 32 center hole walls, an oil inlet A is set.In order to guarantee the sealing property of annular piston 33 and casing 32 formed hydraulic rams, on the disc of the outside of annular piston 33, process a groove that installs seal ring 34 additional.On the face of cylinder, inner side of casing 32, process three equidistant splines, the male splines of the friction lining 35 identical with three structures coordinates respectively.The steel disc 36 that the identical friction lining 35 of three structures is identical with three structures is alternate installation, between friction lining 35 and adjacent steel disc 36, be free-running fit under normal conditions, only have the hydraulic oil of working as to be pressed into hydraulic ram, promoting annular piston 33 moves to right, and while forming enough large thrust, the steel disc 36 that the identical friction lining 35 of three structures is identical with three structures is just in contact with one another and compresses.

Described driving engine 1, motor 2, No. two motors 7 and super capacitor 5 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, as the formula (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.

$P_e=\frac{V_a}{1000{\mathrm{\η}}_t}(\mathrm{Mg}{f}_r+\frac{1}{2}{\mathrm{\ρ}}_a{C}_{D}A{V}_a^2+\mathrm{Mgi})---\left(1\right)$

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 guarantee 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 the torque decoupler between 10 pairs of driving engines 1 of No. two motors and wheel, can guarantee 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 in the speed of a motor vehicle is zero, when the rotating speed of front planetary line 12 is zero, and the maximum functional rotating speed that the maximum speed of a motor 2 can balanced engine, as the formula (2).In formula, ω _{mG1_max}be the maximum speed of a motor 12, 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.

ω _{MG1_max}≥k ₁ω _eexp （2）

Secondly, the torque of the torque of a motor 2 and driving engine 1 should meet the relation suc as formula (3), to guarantee that motor 2 has the rotating speed of enough capacity adjusting driving engines 1.In formula, T _emaxfor the maximum torque of driving engine 1, T _{mG1_max}torque while being motor 2 maximum speed.

T _emax≤k ₁T _{MG1_max} （3）

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, described No. two motors 7 require can provide peak power in limit accelerating mode, to guarantee the tractive performance of car load.Accordingly, in limit accelerating mode, first calculate the surplus power that driving engine overcomes air resistance, rolling resistance and grade resistance horsepower, suc as formula (4), wherein t _ifor driving engine opens time in the machine moment, t _afor accelerating the time constantly of ending, 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).

$P_{e,a}=\frac{1}{(t_a-t_i)}{\∫}_{t_i}^{t_a}(P_{\mathrm{eM}}-P_r)\mathrm{dt}---\left(4\right)$

In addition, need calculate resistance due to acceleration power P _acc, as the formula (5).Finally, the power of No. two motors 7 equals resistance due to acceleration power and deducts driving engine surplus power, as the formula (6).

$P_{\mathrm{acc}}=\frac{\mathrm{\&delta;}\&CenterDot;M\&CenterDot;{\mathrm{<figure-callout\; id="2"\; label="v"\; filenames="HDA00003801659400061.png"\; state="\{\{state\}\}">v</figure-callout>}}^2}{3600\&CenterDot;t_a\&CenterDot;{\mathrm{\&eta;}}_t\&CenterDot;2\&CenterDot;3.6}---\left(5\right)$

P _m=P _acc-P _e,a （6）

In formula (5): δ is correction coefficient of rotating mass, v is the limiting condition end of a period speed of a motor vehicle constantly, is 50km/h.

Secondly, the maximum speed of revolution of No. two motors 7 also should meet the requirement of car load maximum speed, as the formula (7).In formula, i ₂for the formed fixed speed ratio of rear planet row, v _maxfor the maximum speed requiring, be 70km/h herein, r is vehicle wheel roll radius, i _dfor main reduction gear reduction ratio.

${\mathrm{<figure-callout\; id="2"\; label="n\; MG"\; filenames="HDA00003801659400061.png"\; state="\{\{state\}\}">n</figure-callout>}}_{\mathrm{MG}}\&GreaterEqual;i_2\&CenterDot;\frac{v_{\max }}{3.6r}\&CenterDot;\frac{30}{\mathrm{\&pi;}}\&CenterDot;i_d---\left(7\right)$

Finally, the base speed point of No. two motors 7 need be calculated according to the speed of a motor vehicle of the normal operation of vehicle, to guarantee that No. two motors often work in the good region of efficiency.To sum up, the principal parameter that can obtain No. two motors 7 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 5 is aspect power, and requirement should have enough power to meet the requirement of vehicle power, and, in the pick-up time of appointment, the power sum of driving engine 1 and super capacitor 5 should be able to meet the overall power requirement of vehicle limiting condition.Aspect energy, requirement is under limiting condition, in the pick-up time of appointment, the energy that super capacitor 5 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 5 deducts the electric energy total amount that 12, motor can provide for No. two required gross energies of motor 7.According to requiring above, the principal parameter of super capacitor 5 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 system input shaft 14, and system input shaft 14 inserts in the hollow shaft of a motor 2.Before described system input shaft 14 inserts, the centre hole of planet row sun wheel 13 is interior for being rotationally connected, and for reducing the friction drag of connecting surface, installs respectively a sleeve 19 and No. two sleeves 23 at the two ends of front planet row sun wheel 13 additional.The right-hand member of system input shaft 14 is processed as major diameter axle, with the centre hole of front planetary line 12 be interference fit.On the rotation axis of system input shaft 14, process from right to left a long blind hole, and on system input shaft 14, radially process with the equipped part of front planet row sun wheel 13 radial direction through hole that the long blind hole on 2-3 and axis communicates, its effect is conveying lubricating oil.

In addition, described inverter 4 is selected according to the voltage class of a motor 2 and No. two motors 7.Three joints of a described motor 2 connect respectively three alternating current output/out splice going splice x, y, z of inverter 4 by cable, the positive and negative connector of inverter 4 adopts respectively cable to be connected with the both positive and negative polarity of super capacitor 5, and three joints of No. two motors 7 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 described in the utility model is as shown in following table:

Mode of operation	Energy source
		Electric-only mode	Super capacitor	5
Electronic infinite variable speed pattern	Driving engine 1 and super capacitor 5
		Paralleling model	Driving engine 1 and super capacitor 5
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 5, by No. two motors 7, be converted into mechanical energy, 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 and drive separately and combine and drive two spermotypes.The common trait of this two spermotype is: now power-transfer clutch 3 separation, a driving engine 1 horsepower output part is through front planet row, by mechanical path, output to car load drive axle, another part is through front planet row, by a motor 2, be converted into electric power, then by No. two motors 7, be converted into mechanical horsepower 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 5.

The division of two spermotypes is mainly according to the maximum output power of driving engine 1 Optimization Work curve.When 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; When 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 5.

3. paralleling model

When the speed of a motor vehicle is higher, power-transfer clutch 3 engages, the front planet row sun 13 is taken turns locked, whole front planet row is equivalent to a fixed speed ratio, the power of the now driving engine 1 output mechanical path of all flowing through outputs to car load drive axle, there is higher driving efficiency, driving engine 1 can be controlled to efficient region again, there is higher thermal efficiency simultaneously.

4. regenerative brake pattern

Regenerative brake pattern, according to the state of automobile, is divided into motor 7 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 7 maximum braking torques that can provide of No. two motors are provided demand braking torque now, just by No. two motor 10 independent brakes, the regenerating braking energy reclaiming is stored in super capacitor 5.If 10 maximum braking torques that can provide of No. two motors are provided the braking torque of demand, just by No. two motors 10 and mechanical brake Associated brake, part energy is reclaimed by No. two motors 7, is stored in super capacitor, and by mechanical brake, the form with heat energy dissipates another part energy.

The principle features of planetary bimodulus parallel-serial hybrid power system:

1. entire car controller is 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 guarantee that driving engine 1 is operated in optimum efficiency region, guarantee that in super capacitor 5, 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 7, reasonable distribution demand torque between driving engine 1 and No. two motors 7.

2. the function of the motor 2 is here for the rotating speed of adjusting driving engine 1 is 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 7 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 to driving engine 1 torque of the road surface demand torque that causes because of mechanical connection between driving engine 1 and the axle drive shaft of car load.

4. this planetary bimodulus parallel-serial hybrid power system can obtain larger moment transmitting ratio; reduced the torque request of torque decoupler requirement to No. two motors 7; thereby can select peak torque less, No. two less motors 7 of size, are easier to be arranged in car load.

5. according to the height of the speed of a motor vehicle, select joint, the released state of power-transfer clutch 3.After power-transfer clutch 3 separation, this planetary bimodulus parallel-serial hybrid power system can realize paralleling model completely, and now the power of driving engine 1, directly from mechanical path output, has guaranteed higher driving efficiency.

Therefore, guaranteeing 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 when car load dynamic assembly parameter designing, reduced 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 power-transfer clutch 3, can make system under different operating conditions, obtain best combined efficiency.

Claims (7)

1. the electric parallel-serial hybrid power system of planetary bimodulus oil, comprise driving engine (1), a motor (2), inverter (4), super capacitor (5), No. two motors (7), front planet row and rear planet row, it is characterized in that, the described electric parallel-serial hybrid power system of planetary bimodulus oil also comprises power-transfer clutch (3), system output shaft (8) and system input shaft (14)

Driving engine (1) is connected with system input shaft (14) by coupler, a motor (2) empty set is at the left end of system input shaft (14), front planet row is sleeved on the right-hand member of system input shaft (14), the right-hand member of a motor (2) is that spline pair is connected with the left end of front planet row sun wheel (13) in front planet row, before power-transfer clutch (3) is sleeved in front planet row, the left end of planet row sun wheel (13) is that spline pair connects, the right-hand member of front planet row is that spline pair is connected with the left end of system output shaft (8), rear planet row is sleeved on the left end of system output shaft (8), No. two motors (7) empty set is at the right-hand member of system output shaft (8), the left end of No. two motors (7) is that spline pair is connected with the right-hand member of rear 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 the rotation axis conllinear of described system input shaft (14), a motor (2), power-transfer clutch (3), front planet row, rear planet row, No. two motors (7) and system output shaft (8).

3. according to the electric parallel-serial hybrid power system of planetary bimodulus oil claimed in claim 1, it is characterized in that, described power-transfer clutch (3) includes casing (32), annular piston (33), three friction lining (35), three steel disc (36), platen (37), clutch hub (39), spring pedestal (40), four springs (41) and little snap ring (42) that structure is identical that structure is identical that structure is identical;

Described clutch hub (39) is that spline pair is connected with the middle part of front planet row sun wheel (9) in front planet row, the face of cylinder, outside of clutch hub (39) centre hole and three steel disc (36) spline pair connections that structure is identical, spring pedestal (40) is sleeved on the face of cylinder, outside of clutch hub (39) centre hole as being rotationally connected, four identical springs (41) of structure are put into four grooves on spring pedestal (40) successively, it is sliding block joint that annular piston (33) is sleeved on the face of cylinder, outside of casing (32) centre hole, on the left circles ring wall being connected with casing (32) center hole wall, an oil inlet A is set, between the friction lining (35) identical with three structures of the face of cylinder, inner side of casing (32), be that spline pair connects, the steel disc (36) that the identical friction lining (35) of three structures is identical with three structures is alternate installation, between the friction lining (35) that three structures the are identical under normal conditions steel disc (36) identical with three structures, it is free-running fit, right side at the identical friction lining (35) of three structures of the alternate installation steel disc (36) identical with three structures is provided with platen (37).

4. according to the electric parallel-serial hybrid power system of planetary bimodulus oil claimed in claim 3, it is characterized in that, described clutch hub (39) is a ring-type element, the centre hole of clutch hub (39) is the internal splined hole being connected for the stage casing castellated shaft with front planet row sun wheel (13), on the face of cylinder, outside of clutch hub (39), be processed with equally spaced three splines, three splines coordinate with the female splines of steel disc (36);

On the face of cylinder, outside of described clutch hub (39) centre hole, be processed with an annular groove, little snap ring (42) packs in annular groove, and is connected with the contact of spring pedestal (40) right side;

On described spring pedestal (40), be evenly distributed with four for placing the groove of the spring (41) that four structures are identical; On the disc of the outside of annular piston, be processed with a groove that seal ring (34) is installed;

On the inner headed face of described casing (32), process the spline of three three friction linings of equidistant installation (35).

5. according to the electric parallel-serial hybrid power system of a kind of planetary bimodulus oil claimed in claim 1, it is characterized in that, described system output shaft (8) is a stepped shaft, and the left end of system output shaft (8) is the castellated shaft being connected with front planet toothrow snare (20) right-hand member center; In system output shaft (8), the right side of castellated shaft is provided with the flange being connected with the left side contact of rear planet row sun wheel (9), on the rotation axis of system output shaft (8), from left to right process a long blind hole, and on system output shaft (8), radially process with the equipped part of rear planet row sun wheel (9) radial direction through hole for delivery of lubricating oil that the long blind hole on 2～3 and axis communicates, the right-hand member of system output shaft (8) is connected with car load drive axle.

6. according to the electric parallel-serial hybrid power system of a kind of planetary bimodulus oil claimed in claim 1, it is characterized in that, a described motor (2) is spline joint with front planet row sun wheel (13), system input shaft (14) is through the hollow and front planetary line interference fit of front planet row sun wheel (13), the left end of the right-hand member of front planet toothrow circle (11) and front planet toothrow snare (20) is spline joint, and the right-hand member of front planet toothrow snare (20) centre hole adopts spline pair to be connected with the left end of system output shaft (8); Front planetary line (12) forms an assembly set with front planetary line left side (21), and front planetary line left side (21) is connected pawl (43) with front planetary line (12) by front planetary line left side and is welded into one; 4 identical front planet rows of planetary wheels (16) of structure are evenly distributed on front planetary line (12) by front planet rows of planetary wheel bearing pin (17) respectively, the identical front planet rows of planetary wheel outside tooth of (16) and the internal tooth of front planet toothrow circle (11) of 4 structures being arranged on front planetary line (12) is meshed, and 4 the identical front planet rows of planetary wheel inner tines of (16) and teeth of front planet row sun wheel (13) of structure are meshed.

7. according to the electric parallel-serial hybrid power system of a kind of planetary bimodulus oil claimed in claim 1, it is characterized in that, described rear planet row also comprises No. three sleeves (24), No. four sleeves (31) and No. two adjustment pads (30), No. three sleeves (24) and No. four sleeves (31) are arranged on respectively the two ends of rear planet row sun wheel (9), adjusting pad (30) No. two is connected with rear planet row pinion carrier right side (29) bolt, adjust pad (30) empty set for No. two in rear planet row sun wheel (9), and the centre hole of adjusting pad (30) for No. two is coaxial with rear planet row sun wheel (9), rear planet row sun wheel (9) is spline joint with No. two motors (7).

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