CN204726218U - There is the hybrid electric drive system of three clutch automatic gearboxes - Google Patents

Abstract

The utility model discloses the hybrid electric drive system with three clutch automatic gearboxes, exist can not make full use of driving engine for overcoming existing hybrid electric drive system, the gross horsepower of drive motor or drive motor can not operate in the problem in best output characteristic range of speed, it comprises the first power inverter (1), startup/power generation all-in-one machine (2), driving engine (3), four clutches (4), drive motor (39), closed-center system (40), second power inverter (41), three clutch automatic gearboxes (62), four clutches output shaft end gear (5), drive motor output shaft end gear (6) and input shaft end tooth are taken turns (7), input shaft end tooth wheel (7) is arranged on the input shaft (38) of three clutch automatic gearboxes (62), and four clutches output shaft end gear (5), drive motor output shaft end gear (6) are taken turns (7) and engaged successively with input shaft end tooth.

Description

There is the hybrid electric drive system of three clutch automatic gearboxes

Technical field

The utility model relates to a kind of drive system belonging to hybrid vehicle and Automotive transmission technical field, and or rather, the utility model relates to a kind of hybrid electric drive system with three clutch automatic gearboxes.

Background technology

The features such as energy-conservation, the anti-emission carburetor of hybrid electric drive system cause the very big concern of automotive field and become an emphasis of automotive research and exploitation.Change-speed box in hybrid power transmission system ensures that driving engine and drive motor are operated in the critical component in the range of speed of best output characteristic.In hybrid electric drive system configuration, in prior art, the layout of drive motor generally has two kinds of modes: one is before drive motor is placed in change-speed box, one is after drive motor is placed in change-speed box, two kinds of diverse locations of drive motor are corresponding two kinds of different hybrid electric drive system configurations, and respectively have merits and faults.

1, drive motor be placed in change-speed box before configuration, have the following advantages: drive motor has variable deceleration ratio, when machine operation at high speed time, by change reduction ratio make its efficiency remain operating in higher region; But also there is following shortcoming: when the demand power such as starting, acceleration, climbing of vehicle is larger, the driving torque of driving engine and drive motor, power are likely subject to the restriction of the maximum bearing ability of change-speed box, maximum power and moment of torsion are not in full use, and there is power wasting problem;

2, drive motor be placed in change-speed box after configuration, have the following advantages: when the demand power such as starting, acceleration, climbing of vehicle is larger, the maximum drive torque of drive motor and power not limited by the maximum bearing ability of change-speed box, there is not power wasting problem; The drive motor at the low rotational speed advantage such as high, fast response time of efficiency can be fully played; But also have following shortcoming: when motor is in high rotating speed, due to without change speed gear box, do not have variable-speed ratio to cause inefficiency, the moment of torsion being supplied to wheel also can sharply decline.

In prior art, drive motor be placed in change-speed box before configuration and drive motor be placed in change-speed box after configuration do not utilize the gross horsepower of driving engine, drive motor fully or effectively do not control in the range of speed of its best output characteristic.

Summary of the invention

Technical problem to be solved in the utility model overcomes in existing hybrid electric drive system to exist to utilize the gross horsepower of driving engine, drive motor or drive motor can not operate in problem in its best output characteristic range of speed all the time fully, provides a kind of hybrid electric drive system and the control method with three clutch automatic gearboxes.

For solving the problems of the technologies described above, the utility model adopts following technical scheme to realize: the described hybrid electric drive system with three clutch automatic gearboxes comprises the first power inverter, startup/power generation all-in-one machine, driving engine, four clutches, four clutches output shaft end gear, drive motor output shaft end gear, input shaft end tooth wheel, diff, drive motor, closed-center system, the second power inverter and three clutch automatic gearboxes.

The plus terminal of the first power inverter is connected with cell negative terminal electric wire with the plus terminal of closed-center system successively with cell negative terminal, and the plus terminal of the second power inverter is connected with cell negative terminal electric wire with the plus terminal of closed-center system successively with cell negative terminal; The mouth of startup/power generation all-in-one machine and the input end of driving engine adopt V-shape belt to be connected; The driving link of four clutches and the flywheel on driving engine adopt flange to be fixedly connected with, the driven member of four clutches is fixedly connected with by the left end of spline pair with four clutches output shaft, and engine gear is sleeved on the right-hand member of four clutches output shaft for being fixedly connected with; Drive motor output shaft end gear set on the output shaft of drive motor for being fixedly connected with, input shaft end tooth wheel is sleeved on the left end of the input shaft in three clutch automatic gearboxes for being fixedly connected with, and four clutches output shaft end gear, drive motor output shaft end gear and input shaft end tooth are taken turns and be connected with a joggle successively; Motor integrated form jack-plug socket on startup/power generation all-in-one machine is electrically connected with the integrated form wiring input socket of the first power inverter, and the integrated form jack-plug socket on drive motor is electrically connected with the integrated form wiring input socket on the second power inverter; Transmission output shaft in three described clutch automatic gearboxes is fixedly connected with the input end of diff.

Three clutch automatic gearboxes described in technical scheme comprise first clutch group, the first input shaft, second clutch group, reverse gear shaft, the second tween drive shaft, output shaft, the 3rd power-transfer clutch, the first tween drive shaft, the second input shaft, input shaft, No. 1 cylindrical roller bearing, No. 2 cylindrical roller bearings, No. 3 cylindrical roller bearings, No. 4 cylindrical roller bearings, No. 5 cylindrical roller bearings, No. 6 cylindrical roller bearings, No. 7 cylindrical roller bearings and No. 8 cylindrical roller bearings.For being rotationally connected on the left shell wall that input shaft adopts No. 1 cylindrical roller bearing to be arranged on case of transmission, the right-hand member of input shaft is fixedly connected with the center of the first clutch driving drum in first clutch group, the center of the driven drum of the first clutch in first clutch group is fixedly connected with the left end of the first input shaft, the second clutch driving drum of second clutch group is fixedly connected with the first clutch driving drum in first clutch group, second input shaft adopts bearing carrier ring to be contained in the left side of the first input shaft for being rotationally connected, the left end of the second input shaft is fixedly connected with the center of the driven drum of the second clutch of second clutch group, the right-hand member of the first input shaft adopts the 3rd power-transfer clutch to be connected with the left end of transmission output shaft, for being rotationally connected on the right shell body wall that the right-hand member of transmission output shaft adopts No. 6 cylindrical roller bearings to be arranged on case of transmission, input shaft, first clutch group, second clutch group, second input shaft, the rotation axis conllinear of the first input shaft and transmission output shaft.First tween drive shaft adopts No. 7 cylindrical roller bearings and No. 8 cylindrical roller bearings to be arranged on the lower end of gear box casing for being rotationally connected; Second tween drive shaft adopts No. 3 cylindrical roller bearings, No. 5 cylindrical roller bearings are arranged on the upper end of gear box casing for being rotationally connected; Reverse gear shaft adopts No. 2 cylindrical roller bearings, No. 4 cylindrical roller bearings are arranged on gear box casing as being rotationally connected.

Three clutch automatic gearboxes described in technical scheme also include mouth driving gear on reverse gear shaft, reverse gear driven gear, 4th synchro, 4 gear driven gears, 3rd synchro, reverse gear shaft input end driven gear, 3 gear driven gears, second tween drive shaft gear of output end, transmission output shaft driven gear, first tween drive shaft gear of output end, first tween drive shaft, 3 gear driving gears, 1 keeps off/reverses gear gear driving gear, 1 gear driven gear, first synchro, 4 gear driving gears, 2 gear driven gears, 2 gear driving gears, second synchro, second input shaft, input shaft and case of transmission.One keeps off/reverse gear driving gear and three keeps off the right side that driving gear is arranged on the first input shaft; Two gear driving gears and four keep off driving gear and are arranged on the second input shaft, and all driving gears all adopt spline to be fixedly connected with the second input shaft with the first input shaft; 1 gear driven gear, 2 gear driven gear, the first tween drive shaft gear of output end, the first synchro and the second synchros are arranged on the first tween drive shaft; First synchro, the second synchro and the first tween drive shaft adopt spline pair to be fixedly connected with; 1 gear driven gear, 2 gear driven gears adopt bearing and the first tween drive shaft to be rotationally connected.3 gear driven gears, 4 gear driven gears, the secondary driven gear that reverses gear, the 3rd synchro, the 4th synchro are arranged on the second tween drive shaft; 3rd synchro, the 4th synchro adopt spline pair to be fixedly connected with the second tween drive shaft; 3 gear driven gears, 4 gear driven gears adopt bearing and the second tween drive shaft to be rotationally connected with the secondary driven gear that reverses gear; One-level of reversing gear driven gear is arranged on reverse gear shaft with the secondary driving gear that reverses gear; One-level of reversing gear driven gear adopts spline pair to be fixedly connected with reverse gear shaft with the secondary driving gear that reverses gear.

The first tween drive shaft described in technical scheme is positioned at immediately below the first input shaft, the center of gyration line of the first input shaft and the first tween drive shaft is in horizontality in parallel to each other, and be in same vertical plane surface, the distance of the center of gyration line of the first input shaft and the first tween drive shaft is the radius of transmission output shaft driven gear and the radius sum of the first tween drive shaft gear of output end, second tween drive shaft is positioned at the right side of the first input shaft, the center of gyration line of the second tween drive shaft and the first input shaft is in same level in parallel to each other, the distance of the center of gyration line of the second tween drive shaft and the first input shaft is the radius of transmission output shaft driven gear and the radius sum of the second tween drive shaft gear of output end, reverse gear shaft is positioned at the top of the first input shaft and the second tween drive shaft, the center of gyration line of reverse gear shaft and the center of gyration line parallel of the first input shaft and the second tween drive shaft, the distance of the center of gyration line of reverse gear shaft and the center of gyration line of the first input shaft is the radius sum of input end driven gear on the radius of the 1 gear/gear driving gear that reverses gear and reverse gear shaft, the distance of the center of gyration line of reverse gear shaft and the center of gyration line of the second tween drive shaft is the radius of mouth driving gear on reverse gear shaft and the radius sum of the driven gear that reverses gear.

Described in technical scheme one is kept off/is reversed gear driving gear and 1 and keep off driven gear, two and keep off driving gear and 2 and keep off driven gear, three and keep off driving gear and 3 and keep off driven gear, four and keep off driving gear and 4 and keep off driven gear, and keep off/reverse gear driving gear and the mouth driving gear that to reverse gear on one-level driven gear and reverse gear shaft and be all in the driven gear that reverses gear and be often connected with a joggle; Second counter shaft driven gear, transmission output shaft driven gear and the first counter shaft driven gear are in successively and are often connected with a joggle.

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

1. the hybrid electric drive system with three clutch automatic gearboxes described in the utility model can utilize a kind of change-speed box to realize two kinds of different hybrid electric drive system configurations: one is before drive motor is placed in change-speed box, one is after drive motor is placed in change-speed box, and switch two kinds of configurations at any time by control clutch and synchro in the course of the work, to adapt to the requirement of different capacity demand.

2. three clutch automatic gearboxes described in the utility model are directly delivered to output shaft by Article 1 power transmission line, and now the poower flow of drive motor is without change-speed box, achieve the hybrid electric drive system configuration after drive motor is placed in change-speed box.In this kind of power transmission line, the maximum power of driving engine and drive motor and moment of torsion are no longer by the maximum restriction of bearing moment of torsion and power of change-speed box, be applicable in vehicle start, acceleration, operating mode that climbing equipower demand is larger, the gross horsepower of driving engine and drive motor can be given full play to, there is no the situation of power dissipation.

3. three clutch automatic gearboxes described in the utility model also can select power to be delivered to output shaft by second or Article 3 power transmission line, achieve the hybrid electric drive system configuration before drive motor is placed in change-speed box.In this kind of power transmission line, during motor height rotating speed by transmission control in the range of speed of its best output characteristic, keep higher output efficiency.Be applicable to the operating mode when the higher and drive motor of the speed of a motor vehicle participates in when driving, because efficiency under motor height rotating speed can decline, the moment of torsion being supplied to wheel also can decline, and at this moment needs the intervention of change-speed box.

4., when three clutch automatic gearboxes described in the utility model to be selected power by switching between second or Article 3 power transmission line, change-speed box has the advantage of the traditional double clutch automatic gearboxes such as shift speed is fast, smooth gear shifting is good, power failure-free, transmission efficiency are high.

5. the structure of three clutch automatic gearboxes described in the utility model is simple, feature richness, power transmission efficiency are high, be easy to realization, is specially adapted to the hybrid electric drive system of full moment of torsion, high performance demands.

Accompanying drawing explanation

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

Fig. 1 is the schematic diagram with the hybrid electric drive system structure composition of three clutch automatic gearboxes described in the utility model;

Fig. 2 is the schematic diagram of the fourth gear three clutch automatic gearbox structure composition described in the utility model embodiment;

The schematic diagram of the gear that Fig. 3 is fourth gear three clutch automatic gearbox described in the utility model embodiment, input shaft, tween drive shaft and reverse gear shaft assembly relation;

Fig. 4 is double-clutch assembly structure composition schematic diagram in three clutch automatic gearboxes described in the utility model;

Fig. 5 is the first power transmission line schematic diagram of fourth gear three clutch automatic gearbox described in the utility model embodiment;

Fig. 6 is for fourth gear three clutch automatic gearbox described in the utility model embodiment is for the second power transmission line schematic diagram when 1 grade;

Fig. 7 is for fourth gear three clutch automatic gearbox described in the utility model embodiment is for the third power transmission line schematic diagram when 2 grades;

Fig. 8 is the schematic block diagram with annexation between each controller and each subsystem in the control system of the hybrid electric drive system of three clutch automatic gearboxes described in the utility model embodiment;

Fig. 9 is the FB(flow block) that three clutch automatic gearbox power transmission lines described in the utility model control;

In figure: 1. the first power inverter, 2. startup/power generation all-in-one machine, 3. driving engine, 4. four clutches, 5. four clutches output shaft end gear, 6. drive motor output shaft end gear, 7. input shaft end tooth wheel, 8. first clutch group, 9. the first input shaft, 10. second clutch group, mouth driving gear on 11. reverse gear shafts, 12. reverse gear driven gears, 13. the 4th synchros, 14. reverse gear shafts, 15.4 shelves driven gear, 16. the 3rd synchros, 17. reverse gear shaft input end driven gears, 18.3 shelves driven gear, 19. second tween drive shafts, 20. second tween drive shaft gear of output end, 21. wheels, 22. vehicle bridge, 23. transmission output shaft driven gears, 24. transmission output shafts, 25. difies, 26. first tween drive shaft gear of output end, 27. the 3rd power-transfer clutchs, 28. first tween drive shafts, 29.3 shelves driving gear, 30.1 grades/reverse gear driving gear, 31.1 shelves driven gear, 32. first synchros, 33.4 shelves driving gear, 34.2 shelves driven gear, 35.2 shelves driving gear, 36. second synchros, 37. second input shafts, 38. input shafts, 39. drive motor, 40. energy accumulating devices, 41. second power inverters, 42. case of transmissiones, 43.1 number cylindrical roller bearing, 44.2 number cylindrical roller bearing, 45.3 number cylindrical roller bearing, 46.4 number cylindrical roller bearing, 47.5 number cylindrical roller bearing, 48.6 number cylindrical roller bearing, 49.7 number cylindrical roller bearing, 50.8 number cylindrical roller bearing, 51. first clutch driving drum friction lining groups, the driven bulging friction lining group of 52. first clutch, 53. first clutch driving drums, the driven drum of 54. first clutch, 55. second clutch driving drums, the driven drum of 56. second clutch, 57. second clutch driving drum friction lining groups, the driven bulging friction lining group of 58. second clutch, 59. entire car controllers, 60.CAN line, 61. gearbox controllers, 62. 3 clutch automatic gearboxes, 63. other subsystem controllers, 64. other subsystems.

Detailed description of the invention

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

Consult Fig. 1, the described hybrid electric drive system with three clutch automatic gearboxes comprises the first power inverter 1, startup/power generation all-in-one machine 2, driving engine 3, four clutches 4, four clutches output shaft end gear 5, drive motor output shaft end gear 6, drive motor 39, closed-center system 40, second power inverter 41, input shaft end tooth wheel 7, three clutch automatic gearboxes 62, diff 25, vehicle bridge 22, wheel 21; Wherein, four clutches output shaft end gear 5, drive motor output shaft end gear 6, input shaft end tooth wheel 7 form hybrid electric drive system power coupling arrangements.

The input shaft of described power coupling arrangements has two: four clutches output shaft and drive motor 39 output shaft, and output shaft is input shaft 38, and three described clutch automatic gearbox output shafts 24 are mechanically connected with the input end of described diff 25.

Described four clutches 4 is friction clutch, its driving link and engine flywheel adopt that flange is fixedly connected with, driven member is fixedly connected with an input shaft i.e. one end of four clutches output shaft in described power coupling arrangements by spline, require during parameter matching: this power-transfer clutch maximum bears moment of torsion, power need be greater than torque peak, the power that driving engine exports.

Described driving engine 3 is direct injection, small displacement, four cylinders, V-type, naturally aspirated engine petrol, driving engine input end is provided with crank shaft pulley, mouth is provided with flywheel, crank shaft pulley is fixedly connected with by spline with engine crankshaft sponson, this crank shaft pulley outer ring be processed with start/power generation all-in-one machine 2 on the V-type groove of the same number in motor pulley outer ring, driving engine 3 and startup/power generation all-in-one machine 2 parallel-axis type are arranged, the groove of startup/power generation all-in-one machine 2 belt pulley adopts V-shape belt wipe contact to be connected with the crank shaft pulley groove of driving engine 3.

Described first power inverter 1, second power inverter 41 is bidirectional power converter used for electric vehicle, alternating current and direct current (DC) bi-directional conversion can be realized, described two power inverters are provided with input end and mouth, input end has integrated form wiring input socket, and mouth has plus terminal and cell negative terminal, described startup/power generation all-in-one machine 2 is V belt translation formula startup/power generation all-in-one machine, its type is automobile-used BSG series electric excitation synchronous motor, its front end input shaft is provided with motor pulley, motor pulley is fixedly connected with by spline with motor input shaft, this motor pulley is processed with V-type groove, electric machine casing is provided with motor integrated form jack-plug socket, this motor integrated form jack-plug socket is electrically connected with the integrated form wiring input socket of the first power inverter 1, first power inverter 1 mouth has plus terminal and cell negative terminal, be electrically connected with cell negative terminal with the plus terminal of closed-center system 40 respectively,

Described closed-center system 40 is Hybrid Vehicle ni-mh (NiMH) storage battery, be made up of less automobile-used ni-mh (NiMH) the electric power storage cell series and parallel meeting national standard of polylith small volume, voltage and current class, and be fixedly mounted in rectangular cell shell by dividing plate, shell is provided with positive and negative electrode binding post, its voltage is determined by the number of the cell of connecting, and its capacity, electric current are determined by the cell number of parallel connection; Described plus terminal and cell negative terminal adopt electric connection mode to be connected with cell negative terminal with the plus terminal of the first power inverter 1 and the second power inverter 41 mouth respectively.

Described drive motor 39 is automobile-used TYSZ serial rare-earth permanent magnet ac synchronous servo-electric/power generation all-in-one machine, this motor output shaft is processed with A type flat key keyway, the keyway corresponding with described flat key is processed with in drive motor output shaft end gear 6 central through hole, both are connected by A type flat key, drive motor 39 shell is provided with integrated form jack-plug socket, this motor integrated form jack-plug socket is electrically connected with the integrated form wiring input socket of the second power inverter 41, drive motor 39 and driving engine 3 are arranged in parallel, and parallel with input shaft 38; Under vehicle is in drive pattern, it is as electrical motor, and closed-center system 40 is its power supply, and under vehicle is in Brake energy recovery pattern, it charges to closed-center system 40 as electrical generator.

The shape of gear tooth of described power coupling arrangements is involute gear profile, and the ratio of the number of teeth, the ratio of radius equal required transmitting ratio, and each gear is in normal engagement.

The detailed performance parameters such as the transmitting ratio of described driving engine 3, drive motor 39, closed-center system 40, first power inverter 1, second power inverter 41 and power coupling arrangements are all by hybrid vehicle Common Parameters matching technique, carry out coupling according to the actual requirements and obtain.

Consult Fig. 2 to Fig. 4, a kind of fourth gear three clutch automatic gearbox comprises first clutch group 8, first input shaft 9, second clutch group 10, mouth driving gear 11 on reverse gear shaft, reverse gear driven gear 12, 4th synchro 13, reverse gear shaft 14, 4 grades of driven gears 15, 3rd synchro 16, reverse gear shaft input end driven gear 17, 3 grades of driven gears 18, second tween drive shaft 19, second tween drive shaft gear of output end 20, transmission output shaft driven gear 23, output shaft 24, first tween drive shaft gear of output end 26, 3rd power-transfer clutch 27, first tween drive shaft 28, 3 grades of driving gears 29, 1 grade/reverse gear driving gear 30, 1 grade of driven gear 31, first synchro 32, 4 grades of driving gears 33, 2 grades of driven gears 34, 2 grades of driving gears 35, second synchro 36, second input shaft 37, input shaft 38, case of transmission 42, No. 1 cylindrical roller bearing 43, No. 2 cylindrical roller bearings 44, No. 3 cylindrical roller bearings 45, No. 4 cylindrical roller bearings 46, No. 5 cylindrical roller bearings 47, No. 6 cylindrical roller bearings 48, No. 7 cylindrical roller bearings 49, No. 8 cylindrical roller bearings 50.

Described 3rd power-transfer clutch 27 is that DLM3 series Wet-type multi-disc is without slip ring magnetic clutch, its driving link, Passive part are processed with female splines, the correspondingly described right-hand member of the first input shaft 9, the left end of transmission output shaft 24 are processed with male splines, described 3rd power-transfer clutch 27 driving link is fixedly connected with by spline pair with the first input shaft 9 right-hand member, and driven member is inputted (left side) and holds and be fixedly connected with by spline pair with output shaft 24; The first described synchro 32, second synchro 36, the 3rd synchro 16, the 4th synchro 13 are lock ring type inertial type of synchronizer, and concrete model is determined by concrete shifting gear and the diameter of axle that connects;

Described first clutch group 8, second clutch group 10 form double-clutch assembly, its type is multiple-piece dry type clutch, first clutch group 8 comprises first clutch driving drum friction lining group 51, the driven bulging friction lining group 52 of first clutch, first clutch driving drum 53, the driven drum 54 of first clutch, wherein first clutch driving drum friction lining group 51 comprises three identical friction linings, the driven bulging friction lining group 52 of first clutch comprises two identical friction linings, and successively with three alternate layouts of friction lining of first clutch driving drum friction lining group 51, second clutch group 10 comprises second clutch driving drum 55, the driven drum 56 of second clutch, second clutch driving drum friction lining group 57, the driven bulging friction lining group 58 of second clutch, wherein second clutch driving drum friction lining group 57 comprises three identical friction linings, the driven bulging friction lining group 58 of second clutch comprises two identical friction linings, and successively with three alternate layouts of friction lining of second clutch driving drum friction lining group 57, corresponding friction lining group is fixed on corresponding master as shown in the figure, on passive drum, and the radius of first clutch group 8 is greater than the radius of second clutch group 10, input shaft 38 right-hand member is fixedly connected with the center of the first clutch driving drum 53 in first clutch group 8, the center of the driven drum 54 of the first clutch in first clutch group 8 is fixedly connected with the left end of the first input shaft 9, the rotation axis conllinear of the driven drum 54 of input shaft 38, first clutch driving drum 53, first clutch and the first input shaft 9, second clutch group 10 is coaxially arranged with first clutch group 8, the second clutch driving drum 55 of second clutch group 10 is fixedly connected with the first clutch driving drum 53 in first clutch group 8, second input shaft 37 is sleeved on the left side of the first input shaft 9, and the length of the first input shaft 9 is greater than the length of the second input shaft 37, the left end of the second input shaft 37 is fixedly connected with the center of the driven drum 56 of the second clutch of second clutch group 10, the right-hand member of the first input shaft 9 adopts the 3rd power-transfer clutch 27 to be connected by described spline pair with the left end of transmission output shaft 24, for being rotationally connected on the right shell body wall that the right-hand member of transmission output shaft 24 adopts No. 6 cylindrical roller bearings 48 to be arranged on case of transmission 42, input shaft 38, first clutch group 8, second clutch group 10, second input shaft 37, the rotation axis conllinear of the first input shaft 9 and transmission output shaft 24.

Described all shape of gear tooths are involute gear profile, the ratio of all gear mesh numbers of teeth, the ratio of radius equal the transmitting ratio of each gear, each gear transmitting ratio is determined by actual-gear design, the value of each gear transmitting ratio has following rule: 1 gear transmitting ratio is maximum, 4 gear transmitting ratios are minimum, the size of transmitting ratio reduces gradually along with increasing progressively of gear, and wherein maximum transmission ratio is determined by car load acceleration capability, and fastest ratio is determined by vehicle the max speed.

First tween drive shaft 28 two ends are arranged on gear box casing 42 as being rotationally connected by No. 7 cylindrical roller bearings 49, No. 8 cylindrical roller bearings 50; Second tween drive shaft 19 two ends are arranged on gear box casing 42 as being rotationally connected by No. 3 cylindrical roller bearings 45, No. 5 cylindrical roller bearings 47; Reverse gear shaft 14 two ends are arranged on gear box casing 42 as being rotationally connected by No. 2 cylindrical roller bearings 44, No. 4 cylindrical roller bearings 46;

The odd number shelves gear driving gear of three described clutch automatic gearboxes 62 is distributed in the first input shaft 9, and even number shelves gear driving gear is distributed in the second input shaft 37; The active shifting gear that first input shaft 9 is installed comprises one gear/reverse driving gear 30, three and keeps off driving gear 29; One gear/reverse driving gear 30 is used as gear driving gear and a reverse gear one-level driving gear; The active shifting gear that second input shaft 37 is installed comprises two gear driving gears 35, four and keeps off driving gear 33, and all driving gears are all fixedly connected with the second input shaft 37 with the first input shaft 9 by spline.

First tween drive shaft 28 is provided with 1 grade of driven gear, 31,2 grades of driven gear 34, first synchro 32, second synchros 36; First synchro 32, second synchro 36 is directly fixedly connected with by spline with the first tween drive shaft 28; 1 grade of driven gear, 31,2 grades of driven gears 34 are rotationally connected by cylindrical roller bearing and the first tween drive shaft 28;

Second tween drive shaft 19 is provided with 3 grades of driven gears, 18,4 grades of driven gears 15, the 3rd synchro 16, the 4th synchro 13; 3rd synchro 16, the 4th synchro 13 are directly fixedly connected with by spline with the second tween drive shaft 19; 3 grades of driven gears, 18,4 grades of driven gears 15, reverse gear secondary driven gear 12 are rotationally connected by cylindrical roller bearing and the second tween drive shaft 19;

Reverse gear shaft 14 is provided with reverse gear one-level driven gear 17, reverse gear secondary driving gear 11; Reverse gear one-level driven gear 17, reverse gear secondary driving gear 11 are fixedly connected with reverse gear shaft 14 by spline;

A described gear/reverse driving gear 30 and 1 grade of driven gear 31, two keep off driving gear 35 and 2 grades of driven gears 34, three keep off driving gear 29 and 3 grades of driven gears 18, four keep off driving gear 33 and 4 grades of driven gears 15, keep off/reverse driving gear 30 is all in normal engagement with mouth driving gear 11 on reverse gear one-level driven gear 17, reverse gear shaft with reverse gear driven gear 12, the second counter shaft driven gear 20, first counter shaft driven gear 26, transmission output shaft driven gear 23 are also in normal engagement.

Described first synchro 32, second synchro 36, the 3rd synchro 16, the 4th synchro 13 when change-speed box do not work or change-speed box select Article 1 power transmission line be normally open, do not contact with any gear gear ring, be combined with corresponding gear gear ring according to controller demand during work.

Consult Fig. 3, the first described input shaft 9, position relationship between reverse gear shaft 14, second tween drive shaft 19 and the first tween drive shaft 28 are:

First tween drive shaft 28 is positioned at immediately below the first input shaft 9, the center of gyration line of the first input shaft 9 and the first tween drive shaft 28 is in horizontality in parallel to each other, and with being in a vertical plane surface, the distance of the center of gyration line of the first input shaft 9 and the first tween drive shaft 28 is the radius of transmission output shaft driven gear 23 and the radius sum of the first tween drive shaft gear of output end 26, second tween drive shaft 19 is positioned at the right side of the first input shaft 9, the center of gyration line of the second tween drive shaft 19 and the first input shaft 9 is in same level in parallel to each other, the center of gyration distance of the second tween drive shaft 19 and the first input shaft 9 is the radius of transmission output shaft driven gear 23 and the radius sum of the second tween drive shaft gear of output end 20, the position of reverse gear shaft 14 and the first input shaft 9, the position of the second tween drive shaft 19 is relevant, namely reverse gear shaft 14 is positioned at the top of the first input shaft 9 and the second tween drive shaft 19, the center of gyration line of reverse gear shaft 14 and the center of gyration line parallel of the first input shaft 9 and the second tween drive shaft 19, the distance of the center of gyration line of reverse gear shaft 14 and the center of gyration line of the first input shaft 9 is the radius sum of input end driven gear 17 on the radius of 1 grade/reverse gear driving gear 30 and reverse gear shaft, be the radius of mouth driving gear 11 on reverse gear shaft and the radius sum of reverse gear driven gear 12 with the distance of the center of gyration line of the second tween drive shaft 19.

Three described clutch automatic gearboxes 62 have following three kinds of power transmission lines:

Article 1, power transmission line: first clutch group 8 → the first input shaft the 9 → three clutch 27 → output shaft 24;

Article 2 power transmission line: the driven gear → output shaft 24 of corresponding gear on certain gear driving gear → tween drive shaft that first clutch group 8 → the first input shaft 9 → the first input shaft 9 is arranged;

Article 3 power transmission line: the driven gear → output shaft 24 of corresponding gear on certain gear driving gear → tween drive shaft that second clutch group 10 → the second input shaft 37 → the second input shaft 37 is arranged;

Described three clutch automatic gearboxes 62 require when parameter matching: described Article 1 power transmission line maximum bears torque value, magnitude of power and be more than or equal to driving engine and drive motor torque peak sum and power sum respectively;

Consult Fig. 5, power, without any variable gear, by first clutch group 8 → the first input shaft the 9 → three power-transfer clutch 27 → output shaft 24, is directly outputted to diff 25 by the first power transmission line.

Consult Fig. 6, for odd gear 1 grade, the second power transmission line 1 grade of driven gear 31 → synchro 32 → the first tween drive shaft 28 → the first tween drive shaft gear of output end 26 → transmission output shaft driven gear 23 → output shaft 24 on gear/reverse driving gear 30 → the first tween drive shaft 28 on first clutch group 8 → the first input shaft 9 → the first input shaft 9, outputs power to diff 25.

Consult Fig. 7, for even gear 2 grades, the third power transmission line 2 grades of driven gear 34 → the second synchro 36 → the first tween drive shaft 28 → the first tween drive shaft gear of output end 26 → transmission output shaft driven gear 23 → output shafts 24 on 2 gear driving gear 35 → the first tween drive shafts 28 on second clutch group 10 → the second input shaft 37 → the second input shaft 37, output power to diff 25.

Under certain condition, described three clutch automatic gearbox 62 transmission of powers are only when Article 2 and Article 3 power transmission line switch, and its operating characteristic is identical with traditional double clutch automatic gearbox;

Consult Fig. 8, a kind of control system with the hybrid electric drive system of three clutch automatic gearboxes 62 comprises entire car controller 59, each subsystem controller, each subsystem; Described each subsystem controller comprises gearbox controller 61 and other subsystem controllers 63, and described each subsystem refers to three clutch automatic gearboxes 62 and other subsystems 64; Described each subsystem controller is all integrated in each subsystem, and after each subsystem type selecting is determined, described each subsystem controller is also correspondingly determined; Described entire car controller 59 adopts CAN line 60 and each subsystem controller to be interconnected, and each subsystem controller adopts CAN line 60 to be connected with each subsystem, adopts CAN message form mutually to exchange between described all controllers and subsystem;

Described have controller relevant to the control of three clutch automatic gearboxes 62 in the control system of the hybrid electric drive system of three clutch automatic gearboxes 62 and have entire car controller 59, gearbox controller 61; In this control system, entire car controller 59 is the same with conventional hybrid drive system entire car controller, the variate-value needed for gearbox controller 61 is obtained by integrated vehicle control tactics, and result of calculation is passed to gearbox controller 61 by CAN message form, gearbox controller 61 controls described three clutch automatic gearboxes 62 according to the control method of three clutch automatic gearboxes 62;

Consult Fig. 9, the control method of described three clutch automatic gearboxes 62 selects different dynamic transfer route for controlling three described clutch automatic gearboxes 62, control objectives is the synchro of the first clutch group 8 of three clutch automatic gearboxes, second clutch group 10, the 3rd power-transfer clutch 27 and respective notch, and state of a control is separation and the combination of described control objectives.

The step of the control method of three described clutch automatic gearboxes 62 is as follows:

The first step: described entire car controller utilizes described integrated vehicle control tactics to obtain car load demand torque, required three clutch automatic gearbox transmitting ratios according to the speed of a motor vehicle, accelerator travel, brake-pedal travel and battery SOC, exports drive pattern, required gear Gears i.e. 1-4 grades or reverse gear to gearbox controller;

Second step: whole drive mode Mode, the speed of a motor vehicle, required gear that described gearbox controller is sent according to entire car controller determine concrete transfer route, and concrete steps are:

1. when the car load speed of a motor vehicle is less than a certain specific speed value Vmin and drive pattern Mode be pure motorized motions or combination drive pattern time, then select Article 1 power transmission route;

2. otherwise, select transfer route according to position Gears needed for shelves i.e. 1-4 grades or reverse gear, step is:

1) if required gear is even number shelves, Article 3 power transmission line is selected;

2) if required gear is reverse gear, Article 1 power transmission line is selected;

3) if required gear is odd number gear, Article 2 power transmission line is selected;

Described a certain specific speed value Vmin obtains according to the optimization of actual drive motor efficiency characteristic.

3rd step: after described gearbox controller determination power transmission line, sends instruction to first clutch group 8, second clutch group 10, the 3rd power-transfer clutch 27 and respective synchronization device, and order it to be separated or combine, step is:

1. control that first clutch group 8 combines, second clutch group 10 is separated to be combined with the 3rd clutch 27 and realizes Article 1 power transmission line;

2. control that first clutch group 8 combines, the synchro of corresponding gear i.e. 1 grade or 3 grades or reverse gear combines, second clutch group 10 is separated to be separated with the 3rd clutch 27 and realizes Article 2 power transmission line;

3. control that first clutch group 8 is separated, second clutch group 10 combines, the corresponding gear i.e. synchro of 2 grades or 4 grades combines to be separated with the 3rd clutch 27 and realize Article 3 power transmission line.

Claims (5)

1. one kind has the hybrid electric drive system of three clutch automatic gearboxes, it is characterized in that, the described hybrid electric drive system with three clutch automatic gearboxes comprises the first power inverter (1), startup/power generation all-in-one machine (2), driving engine (3), four clutches (4), four clutches output shaft end gear (5), drive motor output shaft end gear (6), input shaft end tooth wheel (7), diff (25), drive motor (39), closed-center system (40), second power inverter (41) and three clutch automatic gearboxes (62),

The plus terminal of the first power inverter (1) is connected with cell negative terminal electric wire with the plus terminal of closed-center system (40) successively with cell negative terminal, and the plus terminal of the second power inverter (41) is connected with cell negative terminal electric wire with the plus terminal of closed-center system (40) successively with cell negative terminal; The mouth of startup/power generation all-in-one machine (2) adopts V-shape belt to be connected with the input end of driving engine (3); The driving link of four clutches (4) adopts flange to be fixedly connected with the flywheel on driving engine (3), the driven member of four clutches (4) is fixedly connected with by the left end of spline pair with four clutches output shaft, and four clutches output shaft end gear (5) is sleeved on the right-hand member of four clutches output shaft for being fixedly connected with; For being fixedly connected with on the output shaft that drive motor output shaft end gear (6) is sleeved on drive motor (39), input shaft end tooth wheel (7) is sleeved on the left end of the input shaft (38) in three clutch automatic gearboxes (62) for being fixedly connected with, and four clutches output shaft end gear (5), drive motor output shaft end gear (6) and input shaft end tooth are taken turns (7) and be connected with a joggle successively; Motor integrated form jack-plug socket on startup/power generation all-in-one machine (2) is electrically connected with the integrated form wiring input socket of the first power inverter (1), and the integrated form jack-plug socket on drive motor (39) is electrically connected with the integrated form wiring input socket on the second power inverter (41); Transmission output shaft (24) in described three clutch automatic gearboxes (62) is fixedly connected with the input end of diff (25).

2. according to the hybrid electric drive system with three clutch automatic gearboxes according to claim 1, it is characterized in that, described three clutch automatic gearboxes (62) comprise first clutch group (8), first input shaft (9), second clutch group (10), reverse gear shaft (14), second tween drive shaft (19), output shaft (24), 3rd power-transfer clutch (27), first tween drive shaft (28), second input shaft (37), input shaft (38), No. 1 cylindrical roller bearing (43), No. 2 cylindrical roller bearings (44), No. 3 cylindrical roller bearings (45), No. 4 cylindrical roller bearings (46), No. 5 cylindrical roller bearings (47), No. 6 cylindrical roller bearings (48), No. 7 cylindrical roller bearings (49) and No. 8 cylindrical roller bearings (50),

For being rotationally connected on the left shell wall that input shaft (38) adopts No. 1 cylindrical roller bearing (43) to be arranged on case of transmission (42), the right-hand member of input shaft (38) is fixedly connected with the center of the first clutch driving drum (53) in first clutch group (8), the center of the driven drum of first clutch (54) in first clutch group (8) is fixedly connected with the left end of the first input shaft (9), the second clutch driving drum (55) of second clutch group (10) is fixedly connected with the first clutch driving drum (53) in first clutch group (8), second input shaft (37) adopts bearing carrier ring to be contained in the left side of the first input shaft (9) for being rotationally connected, the left end of the second input shaft (37) is fixedly connected with the center of the driven drum of second clutch (56) of second clutch group (10), the right-hand member of the first input shaft (9) adopts the 3rd power-transfer clutch (27) to be connected with the left end of transmission output shaft (24), for being rotationally connected on the right shell body wall that the right-hand member of transmission output shaft (24) adopts No. 6 cylindrical roller bearings (48) to be arranged on case of transmission (42), input shaft (38), first clutch group (8), second clutch group (10), second input shaft (37), the rotation axis conllinear of the first input shaft (9) and transmission output shaft (24),

First tween drive shaft (28) adopts No. 7 cylindrical roller bearings (49) and No. 8 cylindrical roller bearings (50) to be arranged on the lower end of gear box casing (42) for being rotationally connected; Second tween drive shaft (19) adopts No. 3 cylindrical roller bearings (45), No. 5 cylindrical roller bearings (47) to be arranged on the upper end of gear box casing (42) for being rotationally connected; Reverse gear shaft (14) adopts No. 2 cylindrical roller bearings (44), No. 4 cylindrical roller bearings (46) to be arranged on gear box casing (42) as being rotationally connected.

3. according to the hybrid electric drive system with three clutch automatic gearboxes described in claim 1 or 2, it is characterized in that, described three clutch automatic gearboxes (62) also include mouth driving gear (11) on reverse gear shaft, reverse gear driven gear (12), 4th synchro (13), 4 gears driven gear (15), 3rd synchro (16), reverse gear shaft input end driven gear (17), 3 gears driven gear (18), second tween drive shaft gear of output end (20), transmission output shaft driven gear (23), first tween drive shaft gear of output end (26), first tween drive shaft (28), 3 gears driving gear (29), 1 keeps off/reverses gear gear driving gear (30), 1 gear driven gear (31), first synchro (32), 4 gears driving gear (33), 2 gears driven gear (34), 2 gears driving gear (35), second synchro (36), second input shaft (37), input shaft (38) and case of transmission (42),

One keeps off/reverse gear driving gear (30) and three keeps off the right side that driving gear (29) is arranged on the first input shaft (9); Two gears driving gear (35) and four keep off driving gear (33) and are arranged on the second input shaft (37), and all driving gears all adopt spline to be fixedly connected with the second input shaft (37) with the first input shaft (9);

1 gear driven gear (31), 2 gears driven gear (34), the first tween drive shaft gear of output end (26), the first synchro (32) are arranged on the first tween drive shaft (28) with the second synchro (36); First synchro (32), the second synchro (36) adopt spline pair to be fixedly connected with the first tween drive shaft (28); 1 gear driven gear (31), 2 gears driven gear (34) adopt bearing and the first tween drive shaft (28) to be rotationally connected;

3 gears driven gear (18), 4 gears driven gear (15), the secondary driven gear (12) that reverses gear, the 3rd synchro (16), the 4th synchro (13) are arranged on the second tween drive shaft (19); 3rd synchro (16), the 4th synchro (13) adopt spline pair to be fixedly connected with the second tween drive shaft (19); 3 gears driven gear (18), 4 gears driven gear (15) adopt bearing and the second tween drive shaft (19) to be rotationally connected with the secondary driven gear (12) that reverses gear; One-level of reversing gear driven gear (17) is arranged on reverse gear shaft (14) with the secondary driving gear (11) that reverses gear; One-level of reversing gear driven gear (17) adopts spline pair to be fixedly connected with reverse gear shaft (14) with the secondary driving gear (11) that reverses gear.

4. according to the hybrid electric drive system with three clutch automatic gearboxes according to claim 3, it is characterized in that, described the first tween drive shaft (28) is positioned at immediately below the first input shaft (9), first input shaft (9) is in horizontality in parallel to each other with the center of gyration line of the first tween drive shaft (28), and be in same vertical plane surface, first input shaft (9) is the radius of transmission output shaft driven gear (23) and the radius sum of the first tween drive shaft gear of output end (26) with the distance of the center of gyration line of the first tween drive shaft (28), second tween drive shaft (19) is positioned at the right side of the first input shaft (9), second tween drive shaft (19) is in same level in parallel to each other with the center of gyration line of the first input shaft (9), second tween drive shaft (19) is the radius of transmission output shaft driven gear (23) and the radius sum of the second tween drive shaft gear of output end (20) with the distance of the center of gyration line of the first input shaft (9), reverse gear shaft (14) is positioned at the top of the first input shaft (9) and the second tween drive shaft (19), the center of gyration line parallel of the center of gyration line of reverse gear shaft (14) and the first input shaft (9) and the second tween drive shaft (19), the distance of the center of gyration line of reverse gear shaft (14) and the center of gyration line of the first input shaft (9) is the radius sum of input end driven gear (17) on the radius of the 1 gear/gear driving gear (30) that reverses gear and reverse gear shaft, the distance of the center of gyration line of reverse gear shaft (14) and the center of gyration line of the second tween drive shaft (19) is the radius of mouth driving gear (11) on reverse gear shaft and the radius sum of the driven gear (12) that reverses gear.

5. according to the hybrid electric drive system with three clutch automatic gearboxes according to claim 3, it is characterized in that, described one keeps off/reverse gear driving gear (30) and 1 keeps off driven gear (31), two gears driving gear (35) keep off driven gear (34) with 2, three gears driving gear (29) keep off driven gear (18) with 3, four gears driving gear (33) keep off driven gear (15) with 4, one keeps off/reverse gear driving gear (30) is all in reverse gear mouth driving gear (11) and the driven gear (12) that reverses gear on one-level driven gear (17) and reverse gear shaft and is often connected with a joggle, second counter shaft driven gear (20), transmission output shaft driven gear (23) and the first counter shaft driven gear (26) are in successively and are often connected with a joggle.