CN203713522U - Hybrid power-driven system and hybrid vehicle - Google Patents
Hybrid power-driven system and hybrid vehicle Download PDFInfo
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- CN203713522U CN203713522U CN201320848897.4U CN201320848897U CN203713522U CN 203713522 U CN203713522 U CN 203713522U CN 201320848897 U CN201320848897 U CN 201320848897U CN 203713522 U CN203713522 U CN 203713522U
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Abstract
The utility model provides a hybrid power-driven system and a hybrid vehicle. The hybrid power-driven system comprises an engine, a first motor, a second motor, a dynamic coupling differential mechanism, a driving device and a power battery, wherein the output shaft of the engine is connected with the shell of the dynamic coupling differential mechanism, the output shaft of the first motor is connected with a bevel gear at the left end of the dynamic coupling differential mechanism, and a bevel gear at the right end of the dynamic coupling differential mechanism and the output shaft of the second motor are respectively connected with the driving device; the hybrid power-driven system further comprises a first clutch used for combining the engine with the first motor and separating the engine from the first clutch of the first motor and a second clutch used for cutting off the power output of the first motor. According to the hybrid power-driven system provided by the utility model, an engine direct-driven model of a driving system is provided with two selectable gears by controlling the first clutch and the second clutch to be engaged and disengaged, so that the transmission efficiency of the system can be improved when the vehicle is driving at high and medium speeds.
Description
Technical field
The utility model belongs to technical field of hybrid power, particularly relates to a kind of hybrid electric drive system and motor vehicle driven by mixed power.
Background technology
Oil and electricity hybrid vehicle has serial mixed power, parallel type hybrid dynamic and series parallel hybrid power by coupled modes.At present market have the most typical series-parallel hybrid electric system be Toyota general sharp this, general sharp this has two typical feature, the one, adopt planetary wheeling mechanism that driving engine, electrical generator and drive motor are carried out to propulsive effort coupling; The 2nd, take the integrated design of two motors and planetary wheeling mechanism.
Show from existing market the hybrid dynamic system that planet gear type combined hybrid system is obviously better than other type, but planetary wheeling mechanism Design of Mechanical Structure, material and process technology are had relatively high expectations, development difficulty is very large, the domestic ability that does not still possess industrialization.The mixed actuation mechanism of integrated design is by fully integrated to motor and satellite gear in addition, and design typification rear motor cannot be revised, and Zhe Tao mechanism is transplanted in other vehicles and needs to redesign.
Hybrid electric drive system of the prior art, can comprise driving engine, electrical generator, motor, differential mechanism, driving device and electrokinetic cell, electrokinetic cell is connected between electrical generator and motor, the pinion carrier (housing) of differential mechanism is connected with the output shaft of driving engine, the left end finishing bevel gear cuter of differential mechanism is connected with the output shaft of electrical generator, and the right-hand member finishing bevel gear cuter of Su Qi mechanism and the output shaft of motor are connected with driving device.Technique scheme, in the time that driving engine drives separately, first the power of driving engine be passed to the pinion carrier (housing) of differential mechanism by engine output shaft, then this power distributes between the left end finishing bevel gear cuter of differential mechanism and right-hand member finishing bevel gear cuter, passes to respectively electrical generator and generates electricity and pass to driving device to drive Vehicle Driving Cycle.In this case, regulate by the rotating speed to electrical generator, can correspondingly regulate the horsepower output of driving engine, make engine operation in optimum regime, improve the fuel economy of driving engine.
But, in technique scheme, in the time that driving engine drives separately, the moment of torsion of driving engine is always dispensed to left end finishing bevel gear cuter and right-hand member finishing bevel gear cuter by the pinion carrier (housing) of differential mechanism, therefore, the hybrid electric drive system that this technical scheme provides is difficult to meet middling speed or the high speed high load capacity operating mode of vehicle in the time that driving engine drives separately, and need to could realize by dynamotor and the coefficient series model of motor or series-parallel connection pattern.
Utility model content
Technical problem to be solved in the utility model is in the time that driving engine drives separately, to be difficult to meet the middling speed of vehicle or the defect of high speed high load capacity operating mode for existing hybrid electric drive system, and a kind of hybrid electric drive system is provided.
It is as follows that the utility model solves the problems of the technologies described above adopted technical scheme:
A kind of hybrid electric drive system is provided, comprise driving engine, the first motor, the second motor, power coupling diff, driving device and the electrokinetic cell for powering to described the first motor and the second motor, the output shaft of described driving engine is connected with the housing of described power coupling diff, the output shaft of described the first motor is connected with the left end finishing bevel gear cuter of described power coupling diff, the right-hand member finishing bevel gear cuter of described power coupling diff and the output shaft of described the second motor are connected with described driving device respectively, described hybrid electric drive system also comprises for combination and the second clutch that separates the first clutch of described driving engine and the first motor and export for blocking the power of described the first motor.
Further, the output shaft of described driving engine is connected with the housing of described power coupling diff by the first gear pair, and described the first gear pair comprises the first driving gear being connected with the output shaft of described driving engine and the first driven gear being connected with the housing of described power coupling diff.
Further, the output shaft of described the first motor is connected with the left end finishing bevel gear cuter of described power coupling diff by the second gear pair, and described the second gear pair comprises the second driving gear being connected with the output shaft of described the first motor and the second driven gear being connected with the left end finishing bevel gear cuter of described power coupling diff.
Further, described driving device comprises the power take-off shaft being connected with the right-hand member finishing bevel gear cuter of described power coupling diff, be connected to the output gear on described power take-off shaft, be connected on described power take-off shaft and be positioned at the main reduction gear at power transfer path rear, drive diff, left half axle and right axle shaft, the power outgoing side of described main reduction gear is connected with the housing of described driving diff, one end of described left half axle and right axle shaft is connected with left end finishing bevel gear cuter and the right-hand member finishing bevel gear cuter of described driving diff respectively, the other end of described left half axle and right axle shaft connects respectively left wheel and the right wheel of vehicle.
Further, described power coupling diff and described driving diff are symmetrical expression bevel differential.
Further, one end of described second clutch is connected with vehicle body, and the other end is connected with output shaft or the rotor of described the first motor.
Further, described hybrid electric drive system also comprises the torsion vibration absorber being connected between described engine crankshaft and output shaft, and described first clutch is arranged between described the first motor and described torsion vibration absorber.
Further, one end of described first clutch is connected with described torsion vibration absorber, and the other end is connected with output shaft or the rotor of described the first motor.
According to hybrid electric drive system of the present utility model, be provided with for combination and the second clutch that separates the first clutch of described driving engine and the first motor and export for blocking the power of the first motor, like this, when electrokinetic cell electric weight is lower and vehicle in the time that middling speed or high speed high load capacity travel, can engage and second clutch disconnection (entering one grade of direct drive pattern of driving engine) by mixed movement controller control first clutch, to make driving engine and the first motor in conjunction with also rotating integratedly, because driving engine and the first motor are connected on the left end finishing bevel gear cuter and housing of power coupling diff, like this, the left end finishing bevel gear cuter of power coupling diff and housing are pinned by first clutch cannot relative motion, power coupling diff does not change the moment of torsion of transmission, the moment of torsion of driving engine and the first motor is directly passed to driving device, middling speed or the required moment of torsion of high speed high load capacity operating mode of vehicle when providing driving engine to drive separately, and when electrokinetic cell electric weight is lower and vehicle in the time that high speed underload travels, can disconnect and second clutch joint (entering the direct drive pattern of driving engine second gear) by mixed movement controller control first clutch, driving engine is separated and the output shaft of the first motor can not rotate with the first motor, because the output shaft of the first motor and the left end finishing bevel gear cuter of power coupling diff are connected, like this, the left end finishing bevel gear cuter of power coupling diff is fixed, the housing of power coupling diff and right-hand member finishing bevel gear cuter produce a speedup degree transmitting ratio, after being lowered, the moment of torsion that driving engine is input to power coupling diff outputs to driving device, be conducive to, under high speed underload, engine speed is stabilized in to high efficiency range.
Therefore, its engine direct pattern of driving of drive system of hybrid power vehicle of the present utility model has two grades can select, improve the system transmission efficiency of vehicle in the time that high speed is travelled, and in middling speed or the high speed high load capacity operating mode of vehicle, do not need by dynamotor and the coefficient series model of motor or series-parallel connection work pattern, therefore the battery volume of electrokinetic cell can be too large, makes drive system of hybrid power vehicle of the present utility model more be suitable for non-plug-in hybrid vehicle.
In addition, the utility model also provides a kind of motor vehicle driven by mixed power, and it comprises above-mentioned hybrid electric drive system.
Further, described motor vehicle driven by mixed power is non-plug-in hybrid vehicle.
Brief description of the drawings
Fig. 1 is the structural representation of the hybrid electric drive system that provides of the utility model one embodiment;
Fig. 2 is the structure diagram of power coupling diff;
Fig. 3 is that the hybrid electric drive system that provides for the utility model one embodiment mechanical energy under electric-only mode is transmitted schematic diagram;
Fig. 4 is that the hybrid electric drive system that provides for the utility model one embodiment mechanical energy under combination drive pattern is transmitted schematic diagram;
Fig. 5 is that the hybrid electric drive system that provides for the utility model one embodiment mechanical energy under one grade of direct drive pattern of driving engine is transmitted schematic diagram;
Fig. 6 is that the hybrid electric drive system that provides for the utility model one embodiment mechanical energy under the direct drive pattern of driving engine second gear is transmitted schematic diagram.
Reference numeral in specification sheets is as follows:
1, driving engine; 11, the output shaft of driving engine; 2, the first motor; 21, the output shaft of the first motor; 3, the second motor; 31, the output shaft of the second motor; 311, gear; 4, power coupling diff; 41, housing; 42, pinion carrier; 43, left end finishing bevel gear cuter; 44, right-hand member finishing bevel gear cuter; 45, satellite gear; 5, driving device; 51, power take-off shaft; 52, output gear; 53, main reduction gear; 54, drive diff; 55, left half axle; 56, right axle shaft; 6, electrokinetic cell; 7, first clutch; 8, second clutch; 9, electric machine controller; 10, mixed movement controller; 200, torsion vibration absorber; 301, the first driving gear; 302, the first driven gear; 401, the second driving gear; 402, the second driven gear.
Detailed description of the invention
Clearer for technical matters, technical scheme and beneficial effect that the utility model is solved, below in conjunction with drawings and Examples, the utility model is described in further detail.Should be appreciated that specific embodiment described herein is only in order to explain the utility model, and be not used in restriction the utility model.
Please one with reference to Fig. 1, the hybrid electric drive system that the utility model one embodiment provides, comprise driving engine 1, the first motor 2, the second motor 3, power coupling diff 4, driving device 5, for the electrokinetic cell 6 of powering to described the first motor 2 and the second motor 3, for combination with separate the first clutch 7 of described driving engine 1 and the first motor 2, for block described the first motor 2 power output second clutch 8, for controlling the electric machine controller 9 of motor rotation and for controlling the mixed movement controller 10 of drive pattern of this drive system.
In the present embodiment, described electric machine controller 9 is connected between the first motor 2 and the second motor 3, to control the running of the first motor 2 and the second motor 3.One end of described electrokinetic cell 6 is electrically connected with electric machine controller 9, power to the first motor 2 and the second motor 3 by electric machine controller 9, or charges to electrokinetic cell 6 by the first motor 2 and the second motor 3 conversely; The other end of described electrokinetic cell 6 is electrically connected with mixed movement controller 10, power to mixed movement controller 10; Described mixed movement controller 10 is electrically connected with driving engine 1 and electric machine controller 9.Like this, the horsepower output (output torque) that mixed movement controller 10 can control engine, and send request to electric machine controller under different driving pattern, to control the rotating speed of target of the first motor 2 and the second motor 3.
In the present embodiment, power coupling diff 4 is conventional symmetrical expression bevel differential.As shown in Figure 2, this diff comprise housing 41, the pinion carrier 42, left end finishing bevel gear cuter 43, the right-hand member finishing bevel gear cuter 44 that are fixedly connected with or are integrally formed with housing 41 and be rotatably connected on the multiple satellite gears 45 that engage in pinion carrier 42 and with left end finishing bevel gear cuter 43 and right-hand member finishing bevel gear cuter 44.
In the present embodiment, as shown in Figures 1 and 2, the output shaft 11 of described driving engine is connected with the housing 41 of described power coupling diff, the output shaft 21 of described the first motor is connected with the left end finishing bevel gear cuter 43 of described power coupling diff, and the right-hand member finishing bevel gear cuter 44 of described power coupling diff and the output shaft 31 of described the second motor are connected with described driving device 5 respectively.
In the present embodiment, described hybrid electric drive system also comprises the torsion vibration absorber 200 being connected between described engine crankshaft and output shaft 11, and described first clutch 7 is arranged between described the first motor 2 and described torsion vibration absorber 200.Torsion vibration absorber 200, for absorbing the vibration of driving engine, is avoided vibration to be passed to output shaft 11.Preferably, one end of described first clutch 7 is connected with described torsion vibration absorber 200, and the other end is connected with output shaft 31 or the rotor of described the first motor.
In the present embodiment, one end of described second clutch 8 is fixedly connected with vehicle body, and the other end is connected with output shaft 31 or the rotor of described the first motor.
Like this, when first clutch 7 engages and second clutch 8 while disconnecting, driving engine 1 and the first motor 2 combine and rotate around the output shaft 1 of driving engine, the housing 41 that is connected to the described power coupling diff on the output shaft 11 of described driving engine be connected to the output shaft 21 of described the first motor 2 or the left end finishing bevel gear cuter 43 of epitrochanterian described power coupling diff and synchronize rotation (there is no relative motion), to be the left end finishing bevel gear cuter 43 of power coupling diff and housing 41 pinned by first clutch 7 cannot relative motion, like this, do not have an effect (power coupling diff 4 is now equivalent to coupler) in the inside of power coupling diff 4, power coupling diff 4 does not change the moment of torsion of transmission, the moment of torsion of driving engine 1 and the first motor 2 is directly passed to driving device 5, and disconnect and second clutch 8 while engaging when first clutch 7, driving engine 1 and the first motor 2 relatively rotate, output shaft 31 or the rotor of the first motor can not rotate relative to vehicle body, the left end finishing bevel gear cuter 43 of power coupling diff is fixed, the housing 41 of power coupling diff and right-hand member finishing bevel gear cuter 44 produce a speedup degree transmitting ratio (the speedup degree transmitting ratio of for example 1:2), after the moment of torsion that driving engine is input to power coupling diff 4 is like this lowered, output to driving device 5.
In the present embodiment, as shown in Figure 1, the output shaft 11 of described driving engine is connected with the housing 41 of described power coupling diff by the first gear pair, described the first gear pair comprises the first driving gear 301 being connected with the output shaft 11 of described driving engine and the first driven gear 302 being connected with the housing 41 of described power coupling diff, by the engaging of the first driving gear 301 and the first driven gear 302, the moment of torsion of driving engine can be passed to the housing 41 of power coupling diff like this.Certainly, in other embodiments, also the output shaft of driving engine 11 directly can be connected with the housing 41 of power coupling diff.
In the present embodiment, as shown in Figure 1, the output shaft 21 of described the first motor is connected with the left end finishing bevel gear cuter 43 of described power coupling diff by the second gear pair, and described the second gear pair comprises the second driving gear 401 being connected with the output shaft 21 of described the first motor and the second driven gear 402 being connected with the left end finishing bevel gear cuter 43 of described power coupling diff.Engaging by the second driving gear 401 and the second driven gear 402 like this, the moment of torsion of the first motor output can be passed to the left end finishing bevel gear cuter 43 of power coupling diff, or the moment of torsion of conversely left end finishing bevel gear cuter 43 being exported passes to the first motor to order about the first electric power generation.Certainly, in other embodiments, also the output shaft of the first motor 21 directly can be connected with the left end finishing bevel gear cuter 43 of power coupling diff.
In the present embodiment, described driving device 5 is conventional structure, as shown in Figure 1, described driving device 5 comprises the power take-off shaft 51 being connected with the right-hand member finishing bevel gear cuter 43 of described power coupling diff, be connected to the output gear 52 on described power take-off shaft 51, be connected on described power take-off shaft 52 and be positioned at the main reduction gear 53 at power transfer path rear, drive diff 54, left half axle 55 and right axle shaft 56, the power outgoing side of described main reduction gear 53 is connected with the housing of described driving diff 54, one end of described left half axle 55 and right axle shaft 56 is connected with left end finishing bevel gear cuter and the right-hand member finishing bevel gear cuter of described driving diff 54 respectively, the other end of described left half axle 56 and right axle shaft 56 connects respectively left wheel and the right wheel of vehicle.
In the present embodiment, on the output shaft 31 of described the second motor, be provided with and described output gear 52 gears in meshs 311, with by power transmission to power take-off shaft 51, or accept the power that power take-off shaft 51 transmits.
As shown in Figures 3 to 6, for the hybrid electric drive system of the utility model above-described embodiment mechanical energy under electric-only mode, combination drive pattern, one grade of direct drive pattern of driving engine and the direct drive pattern of driving engine second gear is transmitted schematic diagram.In Fig. 3 to Fig. 6, it moves towards to represent the bang path of mechanical energy the arrow of heavy line.
Electric-only mode as shown in Figure 3, when vehicle electric energy abundance and vehicle are during in low speed driving, enter electric-only mode, now first clutch 7 and second clutch 8 all disconnect, the drive torque of the second motor 3 engages by gear 311 and output gear 52, be delivered to main reduction gear 53 and drive on diff 54, drive diff 54 outputting powers to left and right semiaxis to drive wheel.Now the first motor 2 need to overcome self resistance contrarotation, prevents that towing astern driving engine 1 from rotating.The target torque of driving engine is 0, and mixed movement controller 10 is to the request moment of the second motor 3
(T
rfor driving requested torque, be to be obtained according to acceleration pedal signal and brake pedal calculated signals by mixed movement controller, i
fEfor the speed ratio of gear 311 and output gear 52, i is main reduction gear ratio), the rotating speed target of the first motor 2 is
(n
m2be the actual speed that the second motor 3 feeds back, i
aCbe the speed ratio of the second driving gear 401 and the second driven gear 402).
Combination drive pattern as shown in Figure 4, in the time that vehicle electric weight is lower and the speed of a motor vehicle is also low, enter combination drive pattern, now first clutch 7 and second clutch 8 all disconnect, driving engine and two motors coordinate driving vehicle, realize the electrodeless variable-speed between driving engine and axle drive shaft (left half axle and right axle shaft).Control flow is for mixed movement controller 10 is according to accelerator open degree, electrokinetic cell SOC(state-of-charge), the actual speed n fed back of the speed of a motor vehicle, the second motor 3
m2and the restriction of electrokinetic cell charging and discharging capabilities, calculating present engine 1 needs the power p producing
eng, then obtain this power p according to engine optimum working curve
engthe rotation speed n of lower engine operation
engand torque T
eng, obtaining engine target rotating speed and moment of torsion by the intersection point of equipower line and engine optimum working curve, the torque request that now mixed movement controller 10 sends to driving engine 1 is T
eng, to the request moment of the second motor 3
the control rotating speed of target of the first motor 2 is
(i
bDbe the speed ratio of the first driving gear 301 and the first driven gear 302).
One grade of direct drive pattern of driving engine as shown in Figure 5, when electrokinetic cell electric weight lower, and vehicle enters one grade of direct drive pattern of driving engine in the time that middling speed or high speed high load capacity travel, now first clutch 7 engages driving engine 1 and the first motor 2 is combined, and second clutch 8 is in off-state.Because driving engine 1 and the first motor 2 are connected respectively left end finishing bevel gear cuter 43 and the housing 41 of power coupling diff, thereby the left end finishing bevel gear cuter 43 of power coupling diff and housing 41 are pinned by first clutch 7, cannot relative motion, the synthetic moment of torsion of driving engine 2 and the first motor 2 is directly delivered to main reduction gear 53 by power take-off shaft 51 and drives on diff 54 (power coupling diff does not change the moment of torsion of transmission), and the drive torque of the second motor 3 is delivered to main reduction gear 53 and is driven on diff 54 by gear 311 and engaging of output gear 52.This pattern first motor 2 and the second motor 3 can be completely output torque (the first motor and the idle running of the second motor) not, driving engine 1 drives separately vehicle, certainly, the effect that the first motor 2 and the second motor 3 also can serve as Load Regulation motor suitably regulates engine load, such the first motor 2 and the second motor 3 reversion generatings, the first motor 2 and the second motor 3 transmit one to driving device 5 and are passed to driving engine 1 moment of torsion that moment of torsion on driving device 5 is contrary, as shown in Fig. 5 heavy line arrow.
The direct drive pattern of driving engine second gear as shown in Figure 6, when vehicle electric weight lower, and in the time that high speed underload travels, enter the direct drive pattern of driving engine second gear, now first clutch is in off-state, and second clutch engages to be fixed the first motor 2 cannot rotate.Because the output shaft of the first motor and the left end finishing bevel gear cuter of power coupling diff are connected, like this, the left end finishing bevel gear cuter of power coupling diff is fixed, the housing of power coupling diff and right-hand member finishing bevel gear cuter produce a speedup degree transmitting ratio (for example 1:2), after the moment of torsion that driving engine is input to power coupling diff is lowered, output to main reduction gear 53 and drive on diff 54, being conducive to, under high speed underload, engine speed is stabilized in to high efficiency range.This pattern second motor 3 can be completely output torque not, driving engine drives separately vehicle, the effect that the second motor 3 also can serve as Load Regulation motor suitably regulates engine load, such the second motor 3 reversion generatings, transmit one to driving device 5 and be passed to driving engine 1 moment of torsion that moment of torsion on driving device 5 is contrary, as shown in Fig. 6 heavy line arrow.
According to the hybrid electric drive system of the utility model above-described embodiment, be provided with for combination and the second clutch that separates the first clutch of described driving engine and the first motor and export for blocking the power of the first motor, like this, when electrokinetic cell electric weight is lower and vehicle in the time that middling speed or high speed high load capacity travel, can engage and second clutch disconnection (entering one grade of direct drive pattern of driving engine) by mixed movement controller control first clutch, to make driving engine and the first motor in conjunction with also rotating integratedly, because driving engine and the first motor are connected on the left end finishing bevel gear cuter and housing of power coupling diff, like this, the left end finishing bevel gear cuter of power coupling diff and housing are pinned by first clutch cannot relative motion, power coupling diff does not change the moment of torsion of transmission, the moment of torsion of driving engine and the first motor is directly passed to driving device, middling speed or the required moment of torsion of high speed high load capacity operating mode of vehicle when providing driving engine to drive separately, and when electrokinetic cell electric weight is lower and vehicle in the time that high speed underload travels, can disconnect and second clutch joint (entering the direct drive pattern of driving engine second gear) by mixed movement controller control first clutch, driving engine is separated and the output shaft of the first motor can not rotate with the first motor, because the output shaft of the first motor and the left end finishing bevel gear cuter of power coupling diff are connected, like this, the left end finishing bevel gear cuter of power coupling diff is fixed, the housing of power coupling diff and right-hand member finishing bevel gear cuter produce a speedup degree transmitting ratio, after being lowered, the moment of torsion that driving engine is input to power coupling diff outputs to driving device, be conducive to, under high speed underload, engine speed is stabilized in to high efficiency range.Therefore, its engine direct pattern of driving of the drive system of hybrid power vehicle of the utility model above-described embodiment has two grades can select, improve the system transmission efficiency of vehicle in the time that high speed is travelled, and in middling speed or the high speed high load capacity operating mode of vehicle, do not need by dynamotor and the coefficient series model of motor or series-parallel connection work pattern, therefore the battery volume of electrokinetic cell can be too large, makes drive system of hybrid power vehicle of the present utility model more be suitable for non-plug-in hybrid vehicle.
In addition, the utility model one embodiment also provide a kind of motor vehicle driven by mixed power, and it comprises above-mentioned hybrid electric drive system.Preferably, described motor vehicle driven by mixed power is non-plug-in hybrid vehicle.Certainly, can be also plug-in hybrid vehicle.
The foregoing is only preferred embodiment of the present utility model; not in order to limit the utility model; all any amendments of doing within spirit of the present utility model and principle, be equal to and replace and improvement etc., within all should being included in protection domain of the present utility model.
Claims (10)
1. a hybrid electric drive system, comprise driving engine, the first motor, the second motor, power coupling diff, driving device and the electrokinetic cell for powering to described the first motor and the second motor, the output shaft of described driving engine is connected with the housing of described power coupling diff, the output shaft of described the first motor is connected with the left end finishing bevel gear cuter of described power coupling diff, the right-hand member finishing bevel gear cuter of described power coupling diff and the output shaft of described the second motor are connected with described driving device respectively, it is characterized in that, described hybrid electric drive system also comprises for combination and the second clutch that separates the first clutch of described driving engine and the first motor and export for blocking the power of described the first motor.
2. hybrid electric drive system according to claim 1, it is characterized in that, the output shaft of described driving engine is connected with the housing of described power coupling diff by the first gear pair, and described the first gear pair comprises the first driving gear being connected with the output shaft of described driving engine and the first driven gear being connected with the housing of described power coupling diff.
3. hybrid electric drive system according to claim 1, it is characterized in that, the output shaft of described the first motor is connected with the left end finishing bevel gear cuter of described power coupling diff by the second gear pair, and described the second gear pair comprises the second driving gear being connected with the output shaft of described the first motor and the second driven gear being connected with the left end finishing bevel gear cuter of described power coupling diff.
4. hybrid electric drive system according to claim 1, it is characterized in that, described driving device comprises the power take-off shaft being connected with the right-hand member finishing bevel gear cuter of described power coupling diff, be connected to the output gear on described power take-off shaft, be connected on described power take-off shaft and be positioned at the main reduction gear at power transfer path rear, drive diff, left half axle and right axle shaft, the power outgoing side of described main reduction gear is connected with the housing of described driving diff, one end of described left half axle and right axle shaft is connected with left end finishing bevel gear cuter and the right-hand member finishing bevel gear cuter of described driving diff respectively, the other end of described left half axle and right axle shaft connects respectively left wheel and the right wheel of vehicle.
5. hybrid electric drive system according to claim 4, is characterized in that, described power coupling diff and described driving diff are symmetrical expression bevel differential.
6. hybrid electric drive system according to claim 1, is characterized in that, one end of described second clutch is connected with vehicle body, and the other end is connected with output shaft or the rotor of described the first motor.
7. according to the hybrid electric drive system described in claim 1 to 6 any one, it is characterized in that, described hybrid electric drive system also comprises the torsion vibration absorber being connected between described engine crankshaft and output shaft, and described first clutch is arranged between described the first motor and described torsion vibration absorber.
8. hybrid electric drive system according to claim 7, is characterized in that, one end of described first clutch is connected with described torsion vibration absorber, and the other end is connected with output shaft or the rotor of described the first motor.
9. a motor vehicle driven by mixed power, is characterized in that, comprises the hybrid electric drive system described in claim 1 to 8 any one.
10. motor vehicle driven by mixed power according to claim 9, is characterized in that, described motor vehicle driven by mixed power is non-plug-in hybrid vehicle.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201320848897.4U CN203713522U (en) | 2013-12-20 | 2013-12-20 | Hybrid power-driven system and hybrid vehicle |
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| CN201320848897.4U CN203713522U (en) | 2013-12-20 | 2013-12-20 | Hybrid power-driven system and hybrid vehicle |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105383282A (en) * | 2015-12-11 | 2016-03-09 | 北京新能源汽车股份有限公司 | Hybrid power system and working method of hybrid power system |
| CN107176025A (en) * | 2017-06-22 | 2017-09-19 | 中通客车控股股份有限公司 | A kind of plug-in hybrid passenger car special engine and control method |
| CN107933285A (en) * | 2017-12-20 | 2018-04-20 | 广州汽车集团股份有限公司 | Novel hybrid coupling mechanism and motor vehicles |
| CN112793415A (en) * | 2021-02-26 | 2021-05-14 | 崔小雷 | Double differential transmission system |
| CN112848871A (en) * | 2021-01-26 | 2021-05-28 | 魏彬 | Power distribution device, hybrid control device, hybrid transmission structure, and hybrid vehicle |
| CN113715800A (en) * | 2020-05-22 | 2021-11-30 | 广州汽车集团股份有限公司 | Controller and control method of vehicle with hybrid power coupling system and vehicle |
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2013
- 2013-12-20 CN CN201320848897.4U patent/CN203713522U/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105383282A (en) * | 2015-12-11 | 2016-03-09 | 北京新能源汽车股份有限公司 | Hybrid power system and working method of hybrid power system |
| CN107176025A (en) * | 2017-06-22 | 2017-09-19 | 中通客车控股股份有限公司 | A kind of plug-in hybrid passenger car special engine and control method |
| CN107933285A (en) * | 2017-12-20 | 2018-04-20 | 广州汽车集团股份有限公司 | Novel hybrid coupling mechanism and motor vehicles |
| US11267332B2 (en) | 2017-12-20 | 2022-03-08 | Guangzhou Automobile Group Co., Ltd. | Hybrid coupling mechanism and motor vehicle |
| CN113715800A (en) * | 2020-05-22 | 2021-11-30 | 广州汽车集团股份有限公司 | Controller and control method of vehicle with hybrid power coupling system and vehicle |
| CN112848871A (en) * | 2021-01-26 | 2021-05-28 | 魏彬 | Power distribution device, hybrid control device, hybrid transmission structure, and hybrid vehicle |
| CN112793415A (en) * | 2021-02-26 | 2021-05-14 | 崔小雷 | Double differential transmission system |
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