CN101513829B - Series-parallel hybrid power driving device - Google Patents
Series-parallel hybrid power driving device Download PDFInfo
- Publication number
- CN101513829B CN101513829B CN2009100371388A CN200910037138A CN101513829B CN 101513829 B CN101513829 B CN 101513829B CN 2009100371388 A CN2009100371388 A CN 2009100371388A CN 200910037138 A CN200910037138 A CN 200910037138A CN 101513829 B CN101513829 B CN 101513829B
- Authority
- CN
- China
- Prior art keywords
- pair
- planetary mechanism
- rotor
- double
- rotor machine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 239000000969 carrier Substances 0.000 claims description 27
- 229920000136 polysorbate Polymers 0.000 claims description 14
- 239000000203 mixture Substances 0.000 claims description 12
- 229910018095 Ni-MH Inorganic materials 0.000 claims description 3
- 229910018477 Ni—MH Inorganic materials 0.000 claims description 3
- 239000002253 acid Substances 0.000 claims description 3
- WHXSMMKQMYFTQS-UHFFFAOYSA-N lithium Chemical group [Li] WHXSMMKQMYFTQS-UHFFFAOYSA-N 0.000 claims description 3
- 229910052744 lithium Inorganic materials 0.000 claims description 3
- 230000005540 biological transmission Effects 0.000 abstract description 24
- 230000001172 regenerating Effects 0.000 abstract 1
- 238000004458 analytical method Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 241000156302 Porcine hemagglutinating encephalomyelitis virus Species 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 230000008929 regeneration Effects 0.000 description 2
- 238000011069 regeneration method Methods 0.000 description 2
- 230000003044 adaptive Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000000875 corresponding Effects 0.000 description 1
- 230000001808 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005211 surface analysis Methods 0.000 description 1
- 238000003786 synthesis reaction Methods 0.000 description 1
- 230000002194 synthesizing Effects 0.000 description 1
- 230000001131 transforming Effects 0.000 description 1
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
Abstract
The invention discloses a series-parallel hybrid power driving device; an input shaft of an engine is connected with an output shaft sequentially by a first level power transmission mechanism formed by a first contrary-turning dual-rotor motor and a first planetary mechanism as well as a second level power transmission mechanism formed by a second contrary-turning dual-rotor motor and a second planetary mechanism; a accumulator battery is respectively and electrically connected with a first machine controller, a second machine controller and a control unit ECU, wherein, the first machine controller and the second machine controller are respectively and electrically connected with the first contrary-turning dual-rotor motor and the second contrary-turning dual-rotor motor. According to the needs of actual road condition, the invention leads the two dual-rotor motors to work in different combining ways, so as to realize multiple working modes such as pure starting mode, pure electric mode, series-parallel mode, energy regenerating brake mode and the like; when the speed ratio range of the system is greatly increased, the function of stepless speed change can be realized.
Description
Technical field
The present invention relates to power transmission and automatic speed-changing system in the hybrid vehicle, specifically be meant the series-parallel hybrid power driving device of one type of 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 is different according to the energy synthesis mode, can be divided into tandem, parallel and series parallel type.Wherein, series parallel type has combined 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 is high, torque converter transmission efficient is 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 realize the optimum matching (best economy or best power performance coupling) of driving engine and electrical motor operation point according to the operation intention of chaufeur; 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; The mechanical continuously-variable transmission (CVT) of some types that just exist at present; 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 ability and the efficient of transmitting torque and power 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 the purposes or the occasion of transmission smaller powers.
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.
Summary of the invention
The objective of the invention 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 series-parallel hybrid power driving device of the automatic stepless speed change function that under various mode of operations, has wide converter speed ratio through being used of planetary mechanism and drg.
The object of the invention is realized through following technical scheme:
A kind of series-parallel hybrid power driving device, planetary mechanism is connected with drive axle through output shaft, and drive axle is connected with drive wheel through two-semiaxle; The input shaft of driving engine changes double-rotor machine through first pair successively and is connected with output shaft with second planetary mechanism composition second stage 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 through axle; First pair of outer rotor that changes double-rotor machine is connected with the sun wheel of first planetary mechanism through 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 through first fixed axis gear pair and second drg.
Described second pair of commentaries on classics double-rotor machine formed second stage 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 through axle; Second pair of outer rotor that changes double-rotor machine is connected with the sun wheel of second planetary mechanism through second fixed axis gear is secondary.
Described second pair of outer rotor that changes double-rotor machine comprises also that through 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 through first fixed axis gear is secondary.
Described output shaft is to be connected through the pinion carrier of first drg with first planetary mechanism.
Described second pair of commentaries on classics double-rotor machine formed second stage 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 through 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 through the sun wheel of the 3rd drg with second planetary mechanism.
Said first drg and second drg are dry type, wet type or magnet stopper.
Said battery pack is lithium cell, Ni-MH battery or lead-acid battery.
Principle of work of the present invention:
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 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 control respectively first fixed axis gear is secondary, second fixed axis gear is secondary state of kinematic motion 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, through three drgs and two kinds of propulsions source are controlled, selects the different working pattern.When engine operation, can change double-rotor machine and second pair of rotating speed and torque of changeing double-rotor machine through 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 invention:
(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 the different working mode operation; 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, through 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 this system can be used for speed ratio is had the various vehicles of demands of different;
(6) apparatus of the present invention 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 in wide variator ratio range, realize the function of automatic stepless speed change 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 accompanying drawing and embodiment the present invention is done further detailed explanation, but embodiment of the present invention 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.Said 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) defines 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 first fixed axis gear secondary 51; i
2It is the transmitting ratio of first fixed axis gear secondary 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 situation 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 situation of not working.
Embodiment 1
As shown in Figure 2, the series-parallel hybrid power driving device 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, secondary 51, second fixed axis gear secondary 52 of first fixed axis gear and a plurality of tachogen.Driving engine 1 is connected with first pair of internal rotor that changes double-rotor machine 41 through input shaft 31, first drg 103, and internal rotor also is connected with the gear ring of first planetary mechanism 61 through axle; The first pair of outer rotor that changes double-rotor machine 41 is connected with the sun wheel of first planetary mechanism 61 through 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 through axle; Second pair of outer rotor that changes double-rotor machine 42 is connected with the sun wheel of second planetary mechanism 62 through secondary the 52, the 3rd drg 101 of second fixed axis gear.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 through 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, control first pair and change double-rotor machine 41 and second pair of commentaries on classics double-rotor machine 42 action, 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 through fixed axis gear secondary 51; Realize that power passes to second pair of end that changes the internal rotor of double-rotor machine 42 in this back of confluxing by the pinion carrier of planetary mechanism 61, the other end of internal rotor then is connected with the gear ring of second planetary mechanism 62, and the second pair of outer rotor that changes double-rotor machine 62 then is connected with the sun wheel of planetary mechanism 62 through fixed axis gear pair 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 kinds of 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 first fixed axis gear secondary 51 is given first planetary mechanism 61 with transmission of power through first pair, and 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 secondary 51 passes to planetary mechanism 61 through 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 second fixed axis gear secondary 52 is given second planetary mechanism 62 with transmission of power are then changeed through second pair in another road, and 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
02＝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 and can know: drg 103 not glancing impact either way belong to the combination drive pattern, by driving engine 1 with to changeing double-rotor machine driven in common vehicle.
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;, the power with second pair of commentaries on classics double-rotor machine 42 passes to the gear ring of first planetary mechanism 61 after converging, 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 first fixed axis gear secondary 51; Through its pinion carrier output; And converge the back through the power that transmission shaft 32 and second pair change double-rotor machine 42 and divide two-way output by its inside and outside rotor; The internal rotor of second pair of commentaries on classics of one road warp double-rotor machine 42 is directly given transmission of power the gear ring of second planetary mechanism 62, and the outer rotor of double-rotor machine 42, the sun wheel that second fixed axis gear secondary 52 passes to second planetary mechanism 62 are then changeed through second pair in another road, and two-way is exported by its pinion carrier after second planetary mechanism 62 confluxes.
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 and can know: two kinds of situation of first drg, 103 glancing impacts all belong to pure motorized motions pattern, by driving engine 1 with two to commentaries on classics double-rotor machine driven in common vehicle
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 secondary transmitting ratio of (2) two cover fixed axis gears is: i
1=i
2=-1/k;
By above assumed condition, can the speed ratio formula under two kinds of patterns be simplified.
1, first drg 103 glancing impact not
In the case; When designing this system according to us one of the purpose that will reach; That is: under various actual conditions,, make engine operation all the time at optimum mode of operation through to changeing the infinite speed variation effect of double-rotor machine; We get engine speed is certain certain value, and two kinds of situation are analyzed.
(1) the 3rd drg 101 glancing impacts
i
o1＝n
e*(1+k)
2/(n
e*(1+k)
2-n
m1)
Can be known by following formula: 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 confirm 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
Statistics by last table can be found out: 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, is that 3300r/min begins from the rotating speed of driving engine 1; 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
02＝n
e*(k*(1+k))
2/(n
e*(1+k
2)
2-n
m1*(1+k
2)-n
m2*k*(1+k))
Similar with 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 confirms 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 here
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 suppose can get all values in its range of speed to changeing double-rotor machine 42, and the ratio coverage of the inequality that satisfies condition:
Ratio coverage under 1 second kind of situation of table 2 embodiment during k=2.3
Statistics by last table can be found out: its ratio change trend 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, is that 3300r/min begins from the rotating speed of driving engine 1; Ratio coverage begins to narrow down; Its ratio coverage 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, 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 with 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.
Through knowing 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 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 ratio change situation and enumerating according to actual condition of service; When each values of parameters and scope not simultaneously; Resulting ratio change scope also is different, in practical application, can get proper parameters as required.
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 through first drg 103; Also be connected with first pair of internal rotor that changes double-rotor machine 41 through 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 through second drg 102; Power is after this confluxes; Gear ring by first planetary mechanism 61 divides the two-way transmission, and the tween drive spindle 32 of leading up to passes to the pinion carrier of second planetary mechanism 62, and another road is then through passing to second pair of internal rotor that changes double-rotor machine 42 with second fixed axis gear secondary 52; The second pair of outer rotor that changes double-rotor machine 42 is then through the 3rd drg 101 transferring power that links to each other with the sun wheel of second planetary mechanism 62; Power passes to drive axle 9 by the gear ring of second planetary mechanism 62 through output shaft 33 after second planetary mechanism 62 confluxes, finally pass 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 situation, that is: driving engine 1 is worked or is not worked.Because principle of work and the embodiment 1 of this embodiment are basic identical, thus below only list the speed ratio relational expression under the various situation.
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 situation:
(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)*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 situation:
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 situation 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 it is basic identical that concrete principle of work and speed ratio calculate with embodiment 1, no longer tires out here and state.
Embodiment 4
As shown in Figure 5, this embodiment has removed drg 103 on the basis of embodiment 2.
First drg 103 that this embodiment is equivalent to embodiment 2 is four kinds of mode of operations of glancing impact not, and its principle of work and speed ratio relation and embodiment's 2 is basic identical, no longer tired here stating.
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 with it with working process, no longer tires out here and states.
Embodiment 6
As shown in Figure 1, this embodiment and embodiment 1 difference are 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 through secondary 51 and second drg 102 of first fixed axis gear.
Through the labor of power flow direction and speed ratio under the various situation of above embodiment, we can find out that can there be following several kinds of mode of operations in this New-type mixed-coupled formula stepless automatic transmission system:
(1) pure motorized motions pattern
Can be known by above analysis: during driving, three kinds of situation 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 through 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
Can be known by 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
Can be known by above analysis: during driving, when drg 103 glancing impact not, four kinds of situation 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 (6)
1. series-parallel hybrid power driving device, planetary mechanism is connected with drive axle through output shaft, and drive axle is connected with drive wheel through two-semiaxle; It is characterized in that the input shaft of driving engine changes double-rotor machine through first pair successively and is connected with output shaft with second planetary mechanism composition second stage 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 through axle; First pair of outer rotor that changes double-rotor machine is connected with the sun wheel of first planetary mechanism through 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 through first fixed axis gear pair and second drg; Described second pair of commentaries on classics double-rotor machine formed second stage 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 through axle; Second pair of outer rotor that changes double-rotor machine is connected with the sun wheel of second planetary mechanism through second fixed axis gear is secondary;
Or 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 through first fixed axis gear is secondary; Described second pair of commentaries on classics double-rotor machine formed second stage 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 also is connected with second pair of internal rotor that changes double-rotor machine through second fixed axis gear is secondary, and second pair of outer rotor that changes double-rotor machine links to each other with the sun wheel of second planetary mechanism.
2. series-parallel hybrid power driving device according to claim 1; It is characterized in that described second pair of outer rotor that changes double-rotor machine comprises also that through 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.
3. series-parallel hybrid power driving device according to claim 1 is characterized in that, described output shaft is to be connected through the pinion carrier of first drg with first planetary mechanism.
4. series-parallel hybrid power driving device according to claim 2 is characterized in that, described second pair of outer rotor that changes double-rotor machine is to link to each other through the sun wheel of the 3rd drg with second planetary mechanism.
5. series-parallel hybrid power driving device according to claim 1 is characterized in that: said first drg and second drg are dry type, wet type or magnet stopper.
6. series-parallel hybrid power driving device according to claim 1 is characterized in that: said battery pack is lithium cell, Ni-MH battery or lead-acid battery.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100371388A CN101513829B (en) | 2009-02-10 | 2009-02-10 | Series-parallel hybrid power driving device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100371388A CN101513829B (en) | 2009-02-10 | 2009-02-10 | Series-parallel hybrid power driving device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101513829A CN101513829A (en) | 2009-08-26 |
| CN101513829B true CN101513829B (en) | 2012-07-18 |
Family
ID=41038508
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009100371388A Active CN101513829B (en) | 2009-02-10 | 2009-02-10 | Series-parallel hybrid power driving device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101513829B (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8618752B2 (en) | 2010-07-21 | 2013-12-31 | Superior Electron, Llc | System, architecture, and method for minimizing power consumption and increasing performance in electric vehicles |
| CN102555769B (en) * | 2012-03-12 | 2014-12-10 | 重庆大学 | Serial-parallel combined type double-motor hybrid power drive assembly with multiple operating modes |
| CN102745059B (en) * | 2012-07-23 | 2016-01-27 | 天津市松正电动汽车技术股份有限公司 | Series-parallel hybrid electric system |
| CN102774265B (en) * | 2012-08-18 | 2015-09-16 | 天津市松正电动汽车技术股份有限公司 | A kind of hybrid electric drive system |
| CN103009992A (en) * | 2012-12-19 | 2013-04-03 | 湖南大学 | Hybrid power system based on novel magnetic-force stepless transmission and double-rotor motor |
| CN103072459B (en) * | 2013-01-18 | 2015-11-25 | 孙宏斌 | Change-speed box, hybrid power system are unified hybrid vehicle |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1945939A (en) * | 2005-12-27 | 2007-04-11 | 中国科学院电工研究所 | Double mechanical port motor and its driving control system |
| CN101028799A (en) * | 2006-03-03 | 2007-09-05 | 中国汽车技术研究中心 | Double-rotor hybrid power device and driving method for 4-wheel-driven automobile |
| CN101318460A (en) * | 2007-06-07 | 2008-12-10 | 奇瑞汽车股份有限公司 | Power assembly of hybrid power automobile |
| CN201400089Y (en) * | 2009-02-10 | 2010-02-10 | 华南理工大学 | Driving device for serial-parallel hybrid electric vehicle |
-
2009
- 2009-02-10 CN CN2009100371388A patent/CN101513829B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1945939A (en) * | 2005-12-27 | 2007-04-11 | 中国科学院电工研究所 | Double mechanical port motor and its driving control system |
| CN101028799A (en) * | 2006-03-03 | 2007-09-05 | 中国汽车技术研究中心 | Double-rotor hybrid power device and driving method for 4-wheel-driven automobile |
| CN101318460A (en) * | 2007-06-07 | 2008-12-10 | 奇瑞汽车股份有限公司 | Power assembly of hybrid power automobile |
| CN201400089Y (en) * | 2009-02-10 | 2010-02-10 | 华南理工大学 | Driving device for serial-parallel hybrid electric vehicle |
Non-Patent Citations (2)
| Title |
|---|
| JP特开2001-157304A 2001.06.08 |
| JP特开2003-111205A 2003.04.11 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101513829A (en) | 2009-08-26 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104786818B (en) | Hybrid electric vehicle series-parallel type double-planetary-gear-train dynamic coupling device and method | |
| CN101480913B (en) | Electronic infinite variable speed parallel type mixed power driving device | |
| CN201423916Y (en) | Driving device used for parallel hybrid electric vehicle | |
| CN101513829B (en) | Series-parallel hybrid power driving device | |
| CN207809033U (en) | Hybrid electric drive system and vehicle | |
| CN204547733U (en) | Two gear variable speed drive systems of the plug-in hybrid-power automobile of single drive motor | |
| CN207809032U (en) | Hybrid electric drive system and vehicle | |
| CN102815198A (en) | HEV (Hybrid Electric Vehicle) driving system based on CVT (Continuously Variable Transmission) | |
| CN101004211A (en) | Multimode transmission system of mixing dynamical automobile | |
| CN104648115A (en) | Two-shift variable speed drive system of plug-in type hybrid vehicle with integrated single-driving motor | |
| CN106994893B (en) | Double planet wheel rows of mixing multimodal fusion power car drive system | |
| CN103770625A (en) | Double-planet row type dynamic coupling mechanism for hybrid electric vehicle | |
| CN101511622A (en) | Power output device and hybrid vehicle | |
| CN108790776A (en) | A kind of mixed power automobile driving device | |
| CN110525194A (en) | Hybrid vehicle power-driven system and its control method | |
| CN201400089Y (en) | Driving device for serial-parallel hybrid electric vehicle | |
| CN109228842A (en) | A kind of mixed power automobile driving system | |
| CN204567263U (en) | Hybrid vehicle series parallel type double-planet train dynamic coupling device | |
| CN106828068A (en) | A kind of energy storage device and its control method for heavy motor vehicle driven by mixed power | |
| CN1888475A (en) | Mechanical and electric mixed electric controlling stepless variable speed driving system | |
| CN108382182A (en) | A kind of double planet wheel rows of mixing multimodal fusion power vehicle power drive system | |
| CN103802654A (en) | Single-motor hybrid driving device | |
| CN107571730B (en) | A kind of power coupler and its operational mode for hybrid vehicle | |
| CN201895565U (en) | Double clutch type full hybrid electric vehicle transmission system | |
| CN208290960U (en) | Hybrid electric drive system and vehicle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |