CN201400089Y - Driving device for serial-parallel hybrid electric vehicle - Google Patents
Driving device for serial-parallel hybrid electric vehicle Download PDFInfo
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- CN201400089Y CN201400089Y CN2009200510969U CN200920051096U CN201400089Y CN 201400089 Y CN201400089 Y CN 201400089Y CN 2009200510969 U CN2009200510969 U CN 2009200510969U CN 200920051096 U CN200920051096 U CN 200920051096U CN 201400089 Y CN201400089 Y CN 201400089Y
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Abstract
The utility model discloses a driving device for a serial-parallel hybrid electric vehicle, the input shaft of an engine of the driving device is connected with the output shaft by sequentially passing through a first-stage power transmission mechanism formed by a first counter-rotating two-rotor motor and a first planet mechanism and a second-stage power transmission mechanism which is formed bya second counter-rotating two-rotor motor and a second planet mechanism; a storage battery pack is electrically connected with a first motor controller, a second motor controller and a control unit ECU respectively, and the first motor controller and the second motor controller are electrically connected with the first counter-rotating two-rotor motor and the second counter-rotating two-rotor motor respectively. According to the requirements of actual road condition, the engine and the two two-rotor motors work with different combining modes, so as to realize a pure engine-on mode, a pure electric mode, a serial-parallel hybrid mode, an energy regeneration brake mode and other working modes; the continuous speed-regulation function of the counter-rotating two-rotor motors can realize stepless speed change while greatly increasing the speed ratio range of the system.
Description
Technical field
The utility model relates to power transmission and the automatic speed-changing system in the hybrid vehicle, specifically is meant the actuating device that is used for the series parallel hybrid power automobile of a class series parallel hybrid power automobile.
Technical background
At present, because the energy and problem of environment, hybrid vehicle (HEV) more and more causes people's attention, becomes a kind of development tendency gradually, is the focus of current automotive field subject study.HEV can be divided into tandem, parallel and series parallel type according to energy synthesis mode difference.Wherein, series parallel type combines the advantage of series and parallel two formulas, is wherein optimum scheme.
No matter and be HEV or traditional combustion engine vehicle, change-speed box is as its power-transmitting part, and the quality of the driving performance of the adjusting of engine characteristics, vehicle is played crucial effects.In existing multiple power drive system, hydraulic mechanical type automatic transmission with hydraulic torque converter (AT) has and does not cut off power shfit, smooth-going, the turbine transformer of starting to the adaptive advantage of resistance, but has shortcomings such as complex structure, manufacture process requirement height, torque converter transmission efficient are low; Electric control mechanical type automatic speed variator (AMT) has driving efficiency height, advantage that power capability is bigger, but is difficult to obtain the perfect drive characteristic of stepless automatic transmission; Because stepless variable drive (CVT) can continuously change speed ratio, make automobile under any operating mode, can be according to the operation intention of chaufeur, realize the optimum matching (best economy or best power performance coupling) of driving engine and electrical motor operation point, thereby effectively reduce discharging, improve fuel economy, dynamic property and the travelling comfort of car load, therefore, become preferred option based on the mixed power electric car of stepless variable drive.
But, mechanical continuously-variable transmission (CVT) with regard to present some types that exist, also because they in fact all are based on frictional transmission, have shortcomings such as on the low side, the available variator ratio range (being the ratio of system's slowest ratio and minimum speed ratio) of the ability of transmitting torque and power and efficient is quite limited, thereby generally only be suitable for power demand and little liter-car and the motor bike of ratio coverage, or other need to transmit the purposes or the occasion of smaller power.
In recent years, along with the rise of electronlmobil, various hybrid power systems are suggested, and what have has realized industrialization.Be typically the hybrid power system of Toyota Company, Ford, General Corporation the most, their common feature is based on the hybrid power system of planetary wheel and single-rotor motor.
The utility model content
The purpose of this utility model is to overcome the shortcoming of prior art, utilization is to changeing the infinite speed variation effect of double-rotor machine, and, be provided at the actuating device that is used for the series parallel hybrid power automobile of the automatic stepless speed change function that under various mode of operations, has wide converter speed ratio by being used of planetary mechanism and drg.
The purpose of this utility model is achieved through the following technical solutions:
A kind of actuating device that is used for the series parallel hybrid power automobile, planetary mechanism is connected with drive axle through output shaft, and drive axle is connected with drive wheel by two-semiaxle; The input shaft of driving engine changes double-rotor machine by first pair successively and is connected with output shaft with second planetary mechanism composition first order power transmitting mechanism with second pair of commentaries on classics double-rotor machine with the first order power transmitting mechanism that first planetary mechanism is formed; Battery pack is electrically connected with first electric machine controller, second electric machine controller and control unit ECU respectively, and first electric machine controller and second electric machine controller change double-rotor machine with first pair respectively and second pair of commentaries on classics double-rotor machine is electrically connected; Be respectively equipped with first tachogen, second tachogen and the 3rd tachogen on input shaft, the tween drive spindle that connects the first order and second stage connecting gear and the output shaft, control unit ECU is connected with first tachogen, second tachogen, the 3rd signals of rotational speed sensor respectively.
Described first pair of first order power transmitting mechanism that changes double-rotor machine and first planetary mechanism composition is: input shaft is connected with first pair of internal rotor that changes double-rotor machine with first drg, and internal rotor also is connected with the gear ring of first planetary mechanism by axle; First pair of outer rotor that changes double-rotor machine is connected with the sun wheel of first planetary mechanism by first fixed axis gear is secondary; Or first pair of outer rotor that changes double-rotor machine is connected with the sun wheel of first planetary mechanism by first fixed axis gear pair and second drg.
Described second pair of commentaries on classics double-rotor machine formed first order power transmitting mechanism with second planetary mechanism and be: the pinion carrier of first planetary mechanism is connected with second pair of internal rotor that changes double-rotor machine through tween drive spindle, and internal rotor also is connected with the gear ring of second planetary mechanism by axle; Second pair of outer rotor that changes double-rotor machine is connected with the sun wheel of second planetary mechanism by second fixed axis gear is secondary.
Described second pair of outer rotor that changes double-rotor machine comprises also that by secondary the connection with the sun wheel of second planetary mechanism of second fixed axis gear the 3rd drg is connected with the sun wheel of second planetary mechanism.
Described first pair of first order power transmitting mechanism that changes double-rotor machine and first planetary mechanism composition is: output shaft is connected with the pinion carrier of first planetary mechanism, and output shaft also is connected with first pair of internal rotor that changes double-rotor machine by first fixed axis gear is secondary.
Described output shaft is to be connected by the pinion carrier of first drg with first planetary mechanism.
Described second pair of commentaries on classics double-rotor machine formed first order power transmitting mechanism with second planetary mechanism and be: the gear ring of first planetary mechanism is connected with tween drive spindle, tween drive spindle is connected with the pinion carrier of second planetary mechanism, tween drive spindle is secondary and second pair of internal rotor that changes double-rotor machine by second fixed axis gear also, and second pair of outer rotor that changes double-rotor machine links to each other with the sun wheel of second planetary mechanism.
Described second pair of outer rotor that changes double-rotor machine is to link to each other by the sun wheel of the 3rd drg with second planetary mechanism.
Described first drg and second drg are dry type, wet type or magnet stopper.
Described battery pack is lithium cell, Ni-MH battery or lead-acid battery.
Principle of work of the present utility model:
Native system adopts first pair of first planetary mechanism that changes double-rotor machine, second pair of commentaries on classics double-rotor machine and have two degree of freedom, second planetary mechanism as main member, get in the three element of first planetary mechanism and second planetary mechanism two as power intake, respectively driving engine, first pair are changeed double-rotor machine and second pair of energy that changes double-rotor machine divides the transmission of confluxing; And fixed axis gear is secondary to be connected with an input end of planetary mechanism because two outer rotors to the commentaries on classics double-rotor machine all pass through, with the 3rd drg, second drg is controlled the first fixed axis gear pair respectively, the state of kinematic motion of the second fixed axis gear pair control two to the outer rotors that change double-rotor machine and with the state of kinematic motion of the input end of the secondary bonded assembly planetary mechanism of its fixed axis gear, utilize first drg to control the state of kinematic motion of input shaft, realizing that driving engine and first pair change double-rotor machine and second pair of multiple array mode of changeing double-rotor machine, thereby system is reached have the purpose of multiple different working modes.Its concrete work is by the control system of the automobile operation conditions current according to automobile, by three drgs and two kinds of propulsions source are controlled, selects different mode of operations.When engine operation, can change double-rotor machine and second pair of rotating speed and torque of changeing double-rotor machine by first electric machine controller and cooresponding with it first pair continuous of adjusting of first electric machine controller, make driving engine always work in optimum state.
Advantage of the present utility model:
(1) this series parallel type stepless automatic transmission system is when engine operation, can make driving engine select optimal working point flexibly according to actual condition, the torque of driving engine directly or by the magnetic field of changeing the double-rotor machine inner and outer rotors is acted on is directly passed to drive axle, reduce the conversion proportion of mechanical energy and electric energy, made the net effciency of system improve;
Whether the braking of (2) three drgs has determined that with the assembled state of the propulsion source of outputting power this system can be with different mode of operation operations, different patterns has different speed ratios and torque output relation, vehicle can be chosen under the different patterns and move according to the effect horse power demand;
(3) this system is employed has stepless shift function to changeing double-rotor machine itself, does not need to add in addition change-speed box, by can realize large-scale stepless shift function under the various patterns to the speed governing effect of changeing double-rotor machine;
(4) structures shape of planetary mechanism its have fixing torque ratio, so the element that we can select to have minimum torque is as the dog point element, the element with maximum torque is as output element, even control easily, can obtain maximum output torque again;
(5) because ratio coverage increases considerably, make that this system can be used for speed ratio is had the different various vehicles that require;
(6) the utility model device merits and faults of mechanical drive and electric tramsmission of comprehensively having sublated, can realize purely electronicly, pure starting, multiple mode of operation such as combination drive, energy regeneration braking, purposes is broad, driving efficiency is higher, layout is flexible, be easy to control, and can select suitable mode of operation realize the function of automatic stepless speed change in wide variator ratio range according to the actual condition demand.
Description of drawings
Fig. 1 is the schematic diagram of embodiment 6.
Fig. 2 is the schematic diagram of embodiment 1.
Fig. 3 is the schematic diagram of embodiment 2.
Fig. 4 is the schematic diagram of embodiment 3.
Fig. 5 is the schematic diagram of embodiment 4.
Fig. 6 is the schematic diagram of embodiment 5.
The specific embodiment
Below in conjunction with drawings and Examples the utility model is described in further detail, but embodiment of the present utility model is not limited thereto.
First drg described in the following embodiment, second drg and the 3rd drg can be dry type, wet type or magnet stopper.Described first drg and second drg and the 3rd drg also can be the drg of monolithic or multi-disc.Battery pack can be lithium cell, Ni-MH battery or lead-acid battery.
Among the following embodiment, be easy analysis, each parameter general symbol(s) is defined as follows: n
eBe engine speed; n
M1Be first pair of rotating speed that changes double-rotor machine 41; n
M2Be second pair of rotating speed that changes double-rotor machine 42; n
S1Be the sun wheel rotating speed of first planetary mechanism 61, n
R1Be the gear ring rotating speed of first planetary mechanism 61, n
C1Be the pinion carrier rotating speed of first planetary mechanism 61, the planet row characteristic parameter k of first planetary mechanism 61
1=n
R1/ n
S1n
S2Be the sun wheel rotating speed of second planetary mechanism 62, n
R2Be the gear ring rotating speed of second planetary mechanism 62, n
C2Be the pinion carrier rotating speed of second planetary mechanism 62, the planet row characteristic parameter k of second planetary mechanism 62
2=n
R2/ n
S2, i
1It is the transmitting ratio of the first fixed axis gear pair 51; i
2It is the transmitting ratio of the first fixed axis gear pair 52; n
e/ n
C2Transmitting ratio for system; i
11, i
12, i
13, i
14Be respectively first drg 103 when not working, work respectively when the not working transmitting ratio of system under four kinds of various combination situations of second drg 102 and the 3rd drg 101; i
21, i
22, i
23When being respectively the work of first drg 103,101 work of the 3rd drg, second drg 102 is not worked and the 3rd drg 101 is not worked, the transmitting ratio of system under 102 work of second drg and the three kinds of situations of not working.
As shown in Figure 2, the actuating device that is used for the series parallel hybrid power automobile in a kind of hybrid vehicle comprises that driving engine 1, first pair change double-rotor machine 41, second pair and change double-rotor machine 42, first planetary mechanism 61, second planetary mechanism 62, first drg 103, second drg 102, the 3rd drg 101, battery pack 13, control unit ECU12, the first fixed axis gear pair 51, second fixed axis gear secondary 52 and a plurality of tachogen.Driving engine 1 is connected with first pair of internal rotor that changes double-rotor machine 41 by input shaft 31, first drg 103, and internal rotor also is connected with the gear ring of first planetary mechanism 61 by axle; The first pair of outer rotor that changes double-rotor machine 41 is connected with the sun wheel of first planetary mechanism 61 by first fixed axis gear secondary 51.The pinion carrier of first planetary mechanism 61 is connected with second pair of internal rotor that changes double-rotor machine 42 through tween drive spindle 32, and internal rotor also is connected with the gear ring of second planetary mechanism 62 by axle; Second pair of outer rotor that changes double-rotor machine 42 is connected with the sun wheel of second planetary mechanism 62 by the second fixed axis gear pair 52, the 3rd drg 101.The pinion carrier of second planetary mechanism 62 is connected with drive axle 9 through output shaft 33, and drive axle 9 is connected with drive wheel 7 by two-semiaxle 8.Battery pack 13 is electrically connected with first electric machine controller 112, second electric machine controller 111 and control unit ECU12 respectively; First electric machine controller 112 and second electric machine controller 111 change double-rotor machine 41 with first pair respectively and second pair of commentaries on classics double-rotor machine 42 is electrically connected.Be respectively equipped with first tachogen 21, second tachogen 22 and the 3rd tachogen 23 on input shaft 31, tween drive spindle 32 and the output shaft 33, control unit ECU12 is connected with second electric machine controller, 111 signals with first tachogen 21, second tachogen 22, the 3rd tachogen 23, first drg 103, the 3rd drg 101, first electric machine controller 112 respectively.
After the rotating speed of input shaft 31, tween drive spindle 32 and output shaft 33 is detected by first tachogen 21, second tachogen 22 and the 3rd tachogen 23, electric signal is passed to control unit ECU12, control unit is controlled first drg 61,62 actions of second drg, and to first electric machine controller 112 and second electric machine controller, 111 output control signals, controlling first pair changes double-rotor machine 41 and second pair of commentaries on classics double-rotor machine 42 action, and implementation pattern is selected and speed-regulating function.
First pair of internal rotor two ends of changeing double-rotor machine 41, one end is connected with driving engine, the other end is connected with the gear ring of planetary mechanism 61, its outer rotor then is connected with the sun wheel of planetary mechanism 62 by fixed axis gear secondary 51, realize that power is passed to an end of the internal rotor of second pair of commentaries on classics double-rotor machine 42 by the pinion carrier of planetary mechanism 61 in this back of confluxing, the other end of internal rotor then is connected with the gear ring of second planetary mechanism 62, the second pair of outer rotor that changes double-rotor machine 62 then is connected with the sun wheel of planetary mechanism 62 by fixed axis gear secondary 52, power passes to drive axle 9 by the pinion carrier of second planetary mechanism 62 through output shaft 33 after this confluxes, finally pass to two 7 powered vehicle of drive wheel.
Below be first drg 103 in the present embodiment, several working conditions when whether the 3rd drg 101 works:
1, first drg 103 glancing impact not
101 brakings of (1) the 3rd drg
In such cases, driving engine 1 and first pair of power that changes double-rotor machine 41 are through the two-way transmission, driving engine 1 and first pair of adapter shaft that changes double-rotor machine 41 are directly with the gear ring of a part of transmission of power to first planetary mechanism 61, another part then changes the outer rotor of double-rotor machine 41 and the sun wheel that the first fixed axis gear pair 51 is given transmission of power first planetary mechanism 61 by first pair, two-way power is exported to transmission shaft 32 by its pinion carrier after this confluxes; Power and second pair change the power that double-rotor machine 42 itself sends and conflux then, and pass to the gear ring of second planetary mechanism 62 through second pair of internal rotor that changes double-rotor machine 42, export to drive axle 9 by its pinion carrier at last.
At this moment, the transmitting ratio of system is:
i
o1＝n
e*(1+k
1)*(1+k
2)/(i
1*k
2*n
m1-n
e*k
2*(i
1-k
1))
(2) the 3rd drgs 101 are not braked
In such cases, driving engine 1 and first pair of power that changes double-rotor machine 41 are through the two-way transmission, driving engine 1 and first pair of adapter shaft that changes double-rotor machine 41 are directly with the gear ring of a part of transmission of power to planetary mechanism 61, another part then changes the outer rotor of double-rotor machine 41 and the sun wheel that fixed axis gear pair 51 passes to planetary mechanism 61 by first pair, after two-way power confluxes, pass to second pair of internal rotor that changes double-rotor machine 42 by its pinion carrier, the power that double-rotor machine 42 outputs own are changeed in second pair of the power link that then passes over divides two-way transmission, one tunnel internal rotor through second pair of commentaries on classics double-rotor machine 42 is directly passed to power the gear ring of second planetary mechanism 62, the outer rotor of double-rotor machine 42 and the sun wheel that the second fixed axis gear pair 52 is given transmission of power second planetary mechanism 62 are then changeed through second pair in another road, two-way power confluxes at second planetary mechanism 62, finally exports to drive axle 9 by its pinion carrier.
At this moment, the transmitting ratio of system is:
i
o2＝n
e*(1+k
1)*(1+k
2)/(i
2*(1+k
1)*n
m2-i
1*n
m1*(i
2-k
2)+n
e*(i
1-k
1)*(i
2-k
2))
More than analyze as can be known: drg 103 not glancing impact either way belong to the combination drive pattern, by driving engine 1 with to changeing the common powered vehicle of double-rotor machine.
2, first drg, 103 glancing impacts
During 101 work of (1) the 3rd drg
When being in this situation, first pair of sun wheel of changeing the power of double-rotor machine 41 through secondary 51 inflows of first fixed axis gear first planetary mechanism 61, export to transmission shaft 32 through its pinion carrier, after converging, the power with second pair of commentaries on classics double-rotor machine 42 passes to the gear ring of first planetary mechanism 61, and by its pinion carrier output.
In such cases, the transmitting ratio of system is:
i
21＝(1+k
1)*(1+k
2)/i
1/k
2
(2) the 3rd drgs 101 are not worked
When being in this situation, the power of first pair of commentaries on classics double-rotor machine 41 passes to the sun wheel of first planetary mechanism 61 through the first fixed axis gear pair 51, through its pinion carrier output, and converge back by in it by transmission shaft 32 and second pair of power that changes double-rotor machine 42, outer rotor divides two-way output, one the tunnel directly gives transmission of power the gear ring of second planetary mechanism 62 through second pair of internal rotor that changes double-rotor machine 42, another road is then by second pair of outer rotor that changes double-rotor machine 42, the second fixed axis gear pair 52 passes to the sun wheel of second planetary mechanism 62, and two-way confluxes the back by its pinion carrier output at second planetary mechanism 62.
In such cases, the transmitting ratio of system is:
i
22＝n
m1*(1+k
1)*(1+k
2)/(i
2*(1+k
1)*n
m2-i
1*n
m1*(i
2-k
2))
More than analyze as can be known: two kinds of situations of first drg, 103 glancing impacts all belong to pure motorized motions pattern, by driving engine 1 and two to changeing the common powered vehicle of double-rotor machine
For the variation relation of speed ratio under each parameter of analysis of further facilitating and the two kinds of patterns, our hypothesis:
The characteristic parameter of (1) two planetary mechanism is equal, and: k
1=k
2=k;
The transmitting ratio of (2) two cover fixed axis gear pairs is: i
1=i
2=-1/k;
By above assumed condition, the speed ratio formula under two kinds of patterns can be simplified.
1, first drg 103 glancing impact not
In the case, one of purpose that will reach when designing this system according to us, that is: under various actual conditions, by infinite speed variation effect to the commentaries on classics double-rotor machine, all the time make engine operation at optimum mode of operation, we get engine speed is certain certain value, and two kinds of situations are analyzed.
(1) the 3rd drg 101 glancing impacts
i
o1＝n
e*(1+k)
2/(n
e*(1+k)
2-n
m1)
By following formula as can be known: when the rotating speed that changes double-rotor machine 41 when driving engine 1 rotating speed and first pair changed within the specific limits, the value of following formula denominator can just can be born, and when its when zero, but the speed ratio approach infinity.The positive and negative of denominator value can determine that we get output and import in the same way, promptly get: n according to the needed output shaft rotary speed direction of reality here
e* (1+k)
2＞n
M1Simultaneously,, do not need infinity because the actual needs speed ratio is also limited, so, can suitably dwindle scope with upper inequality, conditional inquality is become: n
e* (1+k)＞p*n
M1, we get p=21/20 here.Following table 1 is under the driving engine different rotating speeds, and planet row characteristic parameter K ∈ [4/3,4] is to changeing the rotation speed n of double-rotor machine 41
M1∈ [1000,8030], and the ratio coverage of the inequality that satisfies condition:
Ratio coverage under first kind of situation of table 1 embodiment
| Engine speed (r/min) | 1800 | 2300 | 2800 | 3300 | 3800 | 4600 |
| To changeing the speed adjustable range (r/min) of double- |
1000-4610 | 1000-5940 | 1000-7270 | 1000-8030 | 1000-8030 | 1000-8030 |
| Speed ratio i scope | 1.520-25.128 | 1.509-27.896 | 1.502-30.022 | 1.497-15.807 | 1.494-8.192 | 1.490-5.275 |
By the statistics of last table as can be seen: the rotating speed of driving engine 1 is high more, first pair of speed adjustable range that changes double-rotor machine 41 is wide more, and the scope that the speed ratio of this novel system is contained is also wide more, from the rotating speed of driving engine 1 is 3300r/min, ratio coverage begins to narrow down, its ratio coverage this situation why can occur and be because due to first pair of speed adjustable range that changes double-rotor machine 41 be defined, if range of motor speeds is relaxed, also can correspondingly be widened.
(2) the 3rd drgs 101 are glancing impact not
i
o2＝n
e*(k*(1+k))
2/(n
e*(1+k
2)
2-n
m1*(1+k
2)-n
m2*k*(1+k))
Similar to first kind of situation, the rotary speed direction oneself of the positive and negative output shaft according to actual needs of following formula denominator value determines that in order to satisfy the normal switching of system under two kinds of patterns, direction that output shaft is got need be identical with the direction of first kind of pattern, that is: n herein
e* (1+k
2)
2＞n
M1* (1+k
2)+n
M2* k* (1+k); Simultaneously, suitably dwindle scope, conditional inquality is become: n with upper inequality
e* (1+k
2)
2＞p* (n
M1* (1+k
2)+n
M2* k* (1+k)), same, we get p=21/20 here.Following table 2 is under the driving engine different rotating speeds, and when getting planet row characteristic parameter k=2.3, first pair of rotation speed change scope of changeing double-rotor machine 41 and second pair of commentaries on classics double-rotor machine 42 got: n
M1∈ [1000,8030], n
M2∈ [1000,8030], and hypothesis can be got all values in its range of speed and the ratio coverage of the inequality that satisfies condition to changeing double-rotor machine 42:
Ratio coverage under 1 second kind of situation of table 2 embodiment during k=2.3
| Engine speed (r/min) | 1800 | 2300 | 2800 | 3300 | 3800 | 4600 |
| To changeing the speed adjustable range (r/min) of double- |
1000 | 1000-4040 | 1000-7080 | 1000-8030 | 1000-8030 | 1000-8030 |
| Speed ratio i scope | 1.809-26.069 | 1.718-28.567 | 1.665-30.443 | 1.629-9.951 | 1.604-5.629 | 1.576-3.757 |
By the statistics of last table as can be seen: its speed ratio variation tendency and first kind of situation are basic identical, the rotating speed of driving engine 1 is high more, first pair of speed adjustable range that changes double-rotor machine 41 is wide more, and the scope that the speed ratio of this novel system is contained is also wide more, from the rotating speed of driving engine 1 is 3300r/min, ratio coverage begins to narrow down, this situation why can occur and be equally because due to first pair of speed adjustable range that changes double-rotor machine 41 be defined, if range of motor speeds is relaxed, its ratio coverage also can correspondingly be widened.
2, first drg, 103 glancing impacts
First drg, 103 glancing impacts, driving engine 1 is not worked, and this moment, system's speed ratio was defined as: first pair of rotation speed n of changeing double-rotor machine 41
M1With the ratio of the pinion carrier output speed of planetary mechanism 62, that is: n
M1/ n
C2
(1) the 3rd drg 101 glancing impacts
i
21＝-(1+k)
2
During this kind situation, speed ratio constantly increases along with the increase of K value, but first pair of rotation speed n of changeing birotor 41
M1The rotary speed direction of exporting with the pinion carrier of second planetary mechanism 62 is opposite.
(2) the 3rd drgs 101 are glancing impact not
i
22＝-n
m1*(k*(1+k))
2/(k*(1+k)*n
m2+n
m1*(1+k
2))
When this kind situation is similar to last kind situation, first pair of rotation speed n of changeing birotor 41
M1The rotary speed direction of exporting with the pinion carrier of second planetary mechanism 62 is opposite.
For corresponding with last surface analysis, when getting planet row characteristic parameter k=2.3, first pair of rotation speed change scope of changeing double-rotor machine 41 and second pair of commentaries on classics double-rotor machine 42 got: n
M1∈ [1000,8030], n
M2∈ [1000,8030], and the ratio coverage of the inequality that satisfies condition is: 0.8568-7.9622.
By as can be known to the analysis of embodiment 1 various mode of operations, the ratio coverage of combination drive pattern is more than the wide ranges of pure motorized motions pattern, but even so, the speed ratio maxim is also with near with 8 under the pure motorized motions pattern, and the overdrive has reached 0.8568, and this ratio coverage can satisfy the use of most of vehicles.
The special case of more than analyzing concrete work that this embodiment just is described and speed ratio situation of change and enumerating according to actual condition of service, when the value of each parameter and scope not simultaneously, resulting speed ratio variation range also is different, can get suitable parameter as required in actual applications.
Embodiment 2
As shown in Figure 3: this embodiment and general principle Fig. 1 used unit are basic identical, just the connection mode of each parts are adjusted.Driving engine 1 output shaft 31 directly is connected with the pinion carrier of first planetary mechanism 61 by first drg 103, also be connected with first pair of internal rotor that changes double-rotor machine 41 by first fixed axis gear secondary 51, first pair of outer rotor that changes double-rotor machine 41 then is connected with the sun wheel of first planetary mechanism 61 by second drg 102, power is after this confluxes, gear ring by first planetary mechanism 61 divides the two-way transmission, the tween drive spindle 32 of leading up to passes to the pinion carrier of second planetary mechanism 62, another road is then by passing to second pair of internal rotor that changes double-rotor machine 42 with the second fixed axis gear pair 52, the second pair of outer rotor that changes double-rotor machine 42 is then by the 3rd drg 101 transferring power that links to each other with the sun wheel of second planetary mechanism 62, power is after second planetary mechanism 62 confluxes, gear ring by second planetary mechanism 62 passes to drive axle 9 through output shaft 33, finally passes to two 7 powered vehicle of drive wheel.
Whether in the present embodiment, work according to first drg 103, can at first it be divided into two kinds of situations, that is: driving engine 1 is worked or is not worked.Because the principle of work of this embodiment is substantially the same manner as Example 1, thus below only list speed ratio relational expression under the various situations.
When 1, first drg 103 is not worked
During this kind situation, according to the 3rd drg 101, whether second drg 102 works and can be divided into following
Four kinds of situations:
(1) the 3rd drg 101, second drg 102 are all braked
i
11＝k
1*k
2/((1+k
1)*(1+k
2))
102 brakings of (2) second drgs, the 3rd drg 101 is not braked
i
12＝k
1*k
2*n
e/((1+k
1)*(1+k
2)*n
e-k
1*n
m2+i
2*(1+k
1)*n
e)
101 brakings of (3) the 3rd drgs, second drg 102 is not braked
i
13＝k
1*k
2*n
e/((1+k
2)*((1+k
1)*n
e-n
m1+i
1*n
e))
(4) the 3rd drgs 101, second drg 102 are not all braked
i
14＝k
1*k
2*n
e/((1+k
2+i
2)*(((1+k
1)*n
e-n
m1+i
1*n
e))-k
1*n
m2
2, first drg, 103 work
During this kind situation, comprise three kinds of situations:
101 brakings of (1) the 3rd drg, second drg 102 is not braked
i
21＝-k
1*k
2/(1+k
2)
(2) the 3rd drgs 101 are not braked, and second drg 102 is not braked
i
22＝-k
1*k
2/(1+i
2+k
1+k
2)
(3) the 3rd drgs 101 are not braked, 102 brakings of second drg
i
23＝-1/k
2
Embodiment 3
As shown in Figure 4: different is for this embodiment and embodiment 1: removed the 3rd drg 101 among the embodiment 1.
Whether this embodiment brakes the two kinds of situations that are divided into according to first drg 103: the situation of first drg 103 braking is equivalent to second kind of situation of first drg, 103 glancing impacts among the embodiment 1; First drg 103 is the situation of glancing impact not, is equivalent among the embodiment 1 not second kind of situation of glancing impact of first drg 103, and concrete principle of work is substantially the same manner as Example 1 with speed ratio calculating, is not repeated herein.
Embodiment 4
As shown in Figure 5, this embodiment has removed drg 103 on the basis of embodiment 2.
Embodiment 5
As shown in Figure 6: this embodiment has removed the 3rd drg 101 and first drg 103 on the basis of embodiment 1.The mode of operation of this embodiment has only a kind of, is among the embodiment 1 not second kind of situation of glancing impact of first drg 103, and concrete principle is similar to it to working process, is not repeated herein.
Embodiment 6
As shown in Figure 1, this embodiment difference from Example 1 is that the outer rotor of having set up 102, the first pairs of commentaries on classics of second drg double-rotor machine 41 is connected with the sun wheel of first planetary mechanism 61 by secondary 51 and second drg 102 of first fixed axis gear.
By the labor of power flow direction and speed ratio under the various situations of above embodiment, we as can be seen this New-type mixed-coupled formula stepless automatic transmission system following several mode of operation can be arranged:
(1) pure motorized motions pattern
By above analysis as can be known: during driving, three kinds of situations of first drg, 103 glancing impacts all belong to pure motorized motions pattern.During electric-only mode, the power of system is provided by battery pack 13, is used for powered vehicle by first pair of transformation of energy that changes double-rotor machine 41, second pair and change double-rotor machine 42.
(2) the pure drive pattern that starts
As can be known from the above analysis: during driving, first drg 103 not first kind of situation of glancing impact belongs to pure launch modes.The characteristics of this kind pattern are: first pair of commentaries on classics double-rotor machine 41 and second pair of commentaries on classics double-rotor machine 42 do not provide power, and the power of powered vehicle is provided by driving engine 1 fully.
(3) combination drive pattern
By above analysis as can be known: during driving, when drg 103 glancing impact not, four kinds of situations all can be used as the combination drive pattern.The characteristics of this kind pattern are: driving engine 1 and first pair of commentaries on classics double-rotor machine 41 and second pair of one or two while outputting power powered vehicle of changeing in the double-rotor machine 42.
(4) energy regeneration braking mode
When car brakeing deceleration or descending speed limit, power system no longer includes takeoff output, and first pair of commentaries on classics double-rotor machine 41 and second pair of commentaries on classics double-rotor machine 42 are in the anti-generating state that drags, to the battery pack feedback electric energy.At this moment, first drg 103 must be in braking mode, to guarantee that driving engine 1 is not dragged by counter.
Claims (10)
1, the actuating device that is used for the series parallel hybrid power automobile, planetary mechanism is connected with drive axle through output shaft, and drive axle is connected with drive wheel by two-semiaxle; It is characterized in that the input shaft of driving engine changes double-rotor machine by first pair successively and is connected with output shaft with second planetary mechanism composition first order power transmitting mechanism with second pair of commentaries on classics double-rotor machine with the first order power transmitting mechanism that first planetary mechanism is formed; Battery pack is electrically connected with first electric machine controller, second electric machine controller and control unit ECU respectively, and first electric machine controller and second electric machine controller change double-rotor machine with first pair respectively and second pair of commentaries on classics double-rotor machine is electrically connected; Be respectively equipped with first tachogen, second tachogen and the 3rd tachogen on input shaft, the tween drive spindle that connects the first order and second stage connecting gear and the output shaft, control unit ECU is connected with first tachogen, second tachogen, the 3rd signals of rotational speed sensor respectively.
2, the actuating device that is used for the series parallel hybrid power automobile according to claim 1, it is characterized in that, described first pair of first order power transmitting mechanism that changes double-rotor machine and first planetary mechanism composition is: input shaft is connected with first pair of internal rotor that changes double-rotor machine with first drg, and internal rotor also is connected with the gear ring of first planetary mechanism by axle; First pair of outer rotor that changes double-rotor machine is connected with the sun wheel of first planetary mechanism by first fixed axis gear is secondary; Or first pair of outer rotor that changes double-rotor machine is connected with the sun wheel of first planetary mechanism by first fixed axis gear pair and second drg.
3, the actuating device that is used for the series parallel hybrid power automobile according to claim 2, it is characterized in that, described second pair of commentaries on classics double-rotor machine formed first order power transmitting mechanism with second planetary mechanism and be: the pinion carrier of first planetary mechanism is connected with second pair of internal rotor that changes double-rotor machine through tween drive spindle, and internal rotor also is connected with the gear ring of second planetary mechanism by axle; Second pair of outer rotor that changes double-rotor machine is connected with the sun wheel of second planetary mechanism by second fixed axis gear is secondary.
4, the actuating device that is used for the series parallel hybrid power automobile according to claim 3, it is characterized in that described second pair of outer rotor that changes double-rotor machine comprises also that by secondary the connection with the sun wheel of second planetary mechanism of second fixed axis gear the 3rd drg is connected with the sun wheel of second planetary mechanism.
5, the actuating device that is used for the series parallel hybrid power automobile according to claim 1, it is characterized in that, described first pair of first order power transmitting mechanism that changes double-rotor machine and first planetary mechanism composition is: output shaft is connected with the pinion carrier of first planetary mechanism, and output shaft also is connected with first pair of internal rotor that changes double-rotor machine by first fixed axis gear is secondary.
6, the actuating device that is used for the series parallel hybrid power automobile according to claim 5 is characterized in that, described output shaft is to be connected by the pinion carrier of first drg with first planetary mechanism.
7, according to claim 5 or the 6 described actuating devices that are used for the series parallel hybrid power automobile, it is characterized in that, described second pair of commentaries on classics double-rotor machine formed first order power transmitting mechanism with second planetary mechanism and be: the gear ring of first planetary mechanism is connected with tween drive spindle, tween drive spindle is connected with the pinion carrier of second planetary mechanism, tween drive spindle is secondary and second pair of internal rotor that changes double-rotor machine by second fixed axis gear also, and second pair of outer rotor that changes double-rotor machine links to each other with the sun wheel of second planetary mechanism.
8, the actuating device that is used for the series parallel hybrid power automobile according to claim 7 is characterized in that, described second pair of outer rotor that changes double-rotor machine is to link to each other by the sun wheel of the 3rd drg with second planetary mechanism.
9, according to claim 2, the 3 or 4 described actuating devices that are used for the series parallel hybrid power automobile, it is characterized in that: described first drg and second drg are dry type, wet type or magnet stopper.
10, the actuating device that is used for the series parallel hybrid power automobile according to claim 1 is characterized in that: described battery pack is lithium cell, Ni-MH battery or lead-acid battery.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200510969U CN201400089Y (en) | 2009-02-10 | 2009-02-10 | Driving device for serial-parallel hybrid electric vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200510969U CN201400089Y (en) | 2009-02-10 | 2009-02-10 | Driving device for serial-parallel hybrid electric vehicle |
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| Publication Number | Publication Date |
|---|---|
| CN201400089Y true CN201400089Y (en) | 2010-02-10 |
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ID=41659884
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009200510969U Expired - Lifetime CN201400089Y (en) | 2009-02-10 | 2009-02-10 | Driving device for serial-parallel hybrid electric vehicle |
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| CN (1) | CN201400089Y (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101870256A (en) * | 2010-06-17 | 2010-10-27 | 同济大学 | Wheel-sdie mixed drive device of engineering mechanical traveling system |
| CN101985274A (en) * | 2010-11-12 | 2011-03-16 | 北京航空航天大学 | Five-gear automatic transmission-based hybrid vehicle transmission system |
| CN101513829B (en) * | 2009-02-10 | 2012-07-18 | 华南理工大学 | Series-parallel hybrid power driving device |
| CN104742749A (en) * | 2015-03-27 | 2015-07-01 | 河北御捷车业有限公司 | Electric automobile chassis |
| 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 |
| CN108189660A (en) * | 2018-02-28 | 2018-06-22 | 重庆交通大学 | Electric coupling apparatus is cascaded for the multiaxis of hybrid vehicle |
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2009
- 2009-02-10 CN CN2009200510969U patent/CN201400089Y/en not_active Expired - Lifetime
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101513829B (en) * | 2009-02-10 | 2012-07-18 | 华南理工大学 | Series-parallel hybrid power driving device |
| CN101870256A (en) * | 2010-06-17 | 2010-10-27 | 同济大学 | Wheel-sdie mixed drive device of engineering mechanical traveling system |
| CN101870256B (en) * | 2010-06-17 | 2012-12-05 | 同济大学 | Wheel-side mixed drive device of engineering mechanical traveling system |
| CN101985274A (en) * | 2010-11-12 | 2011-03-16 | 北京航空航天大学 | Five-gear automatic transmission-based hybrid vehicle transmission system |
| CN101985274B (en) * | 2010-11-12 | 2012-12-19 | 北京航空航天大学 | Five-gear automatic transmission-based hybrid vehicle transmission system |
| CN104742749A (en) * | 2015-03-27 | 2015-07-01 | 河北御捷车业有限公司 | Electric automobile chassis |
| 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 |
| CN107933285B (en) * | 2017-12-20 | 2019-10-18 | 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 |
| CN108189660A (en) * | 2018-02-28 | 2018-06-22 | 重庆交通大学 | Electric coupling apparatus is cascaded for the multiaxis of hybrid vehicle |
| CN108189660B (en) * | 2018-02-28 | 2023-12-12 | 重庆交通大学 | Multi-shaft cascading electromechanical coupling device for hybrid electric vehicle |
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| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: Guangzhou GAC Group Motor Co., Ltd. Assignor: South China University of Technology| Guangzhou Automobile Group Co Contract record no.: 2011440000278 Denomination of utility model: Driving device for serial-parallel hybrid electric vehicle Granted publication date: 20100210 License type: Exclusive License Record date: 20110401 |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20100210 Effective date of abandoning: 20090210 |