CN106042890A - Hybrid power transmission device - Google Patents
Hybrid power transmission device Download PDFInfo
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- CN106042890A CN106042890A CN201610410620.1A CN201610410620A CN106042890A CN 106042890 A CN106042890 A CN 106042890A CN 201610410620 A CN201610410620 A CN 201610410620A CN 106042890 A CN106042890 A CN 106042890A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
- B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Electric Propulsion And Braking For Vehicles (AREA)
- Hybrid Electric Vehicles (AREA)
Abstract
The invention provides a hybrid power transmission device. The hybrid power transmission device comprises a small motor (EM1), a large motor (EM2), a double-row planet gear mechanism and a two-stage speed reducing gear system. The hybrid power transmission device is also provided with a first brake (B1), a second brake (B2), a third brake (B3), a first clutch (C0) and a second clutch (C1), so that a plurality of pure electric driving modes and a plurality of hybrid power driving modes are realized. When the hybrid power transmission device is in the pure electric driving mode, the clutch C0 is opened to separate an engine, and the pure electric driving modes of three gear shiftings are realized through controlling the brake B1, the brake B2 and the brake B3 to close or open; and when the clutch C0 is closed, the engine participates in working and is in the hybrid power driving mode, and the brake B1, the brake B2, the brake B3, and the clutch C1 are in coordination control to realize the hybrid power driving modes and power branching driving modes in a plurality of fixed rotation ratios. The hybrid power transmission device disclosed by the invention is compact in structure, belongs to a platformization technical scheme, and can be applied to an advanced hybrid power system and a plugging-in hybrid power system.
Description
Technical field
The present invention relates to a kind of automobile actuating device, particularly to a kind of hybrid transmissions.
Background technology
Along with country's new-energy automobile strategy development and the aggravation of environmental energy problem so that Ge great motor corporation is all
Actively researching and developing energy-saving and environment-friendly automobile, technically the hybrid power system of comparative maturity become present stage solve automobile energy consumption and
The possible technique scheme of environmental pollution, its core drive actuating device the most just becomes the emphasis of each company research and development.
The most more technical scheme is both for single platform application, is respectively used to hybrid power system or plug-in mixes
Close dynamical system, be difficult to apply simultaneously to multiple car load platform.Therefore, when power transmission solution designs, development platform
Technical scheme needs not only to meet the lift-launch demand of different dynamic system, in addition it is also necessary to can shorten the exploitation week of subsequent serial product
Phase.
Summary of the invention
It is desirable to provide a kind of compact conformation, hardware and software platform are applied and have the hybrid power transmission of multiple-working mode
Device.
The present invention is realized by below scheme:
A kind of hybrid transmissions, including small machine EM1, big motor EM2, differential mechanism, power shaft, also includes first
Single planetary row PG1, the second single planetary row PG2, the first brake B1, second brake B2, the 3rd brake B3, the first reducing gear
Wheel Z1, big retarding gear Z2 and little reduction gearing Z3, the first single planetary row PG1 include the first sun gear S1, the first row star-wheel P1,
The first row carrier PC1 and the first external toothing R1, the second single planetary row PG2 include the second sun gear S2, the second planetary gear P2, second
Planet carrier PC2 and the second external toothing R2, the first single planetary row PG1 and the second single planetary row PG2 double planet of composition placed side by side
Gear mechanism, the first row carrier PC1 of the first single planetary row and the second sun gear S2 of the second single planetary row are connected to form
One axle, the first external toothing R1 of the first single planetary row and the second planet carrier PC2 of described second single planetary row are connected to form the
Two axles, the second axle is as the output shaft of compound planetary gearing；Second axle is installed the first reduction gearing Z1, big retarding tooth
Wheel Z2 is connected by rotating shaft with little reduction gearing Z3, and the first reduction gearing Z1 is meshed with big retarding gear Z2 the formation first order
Reducing gear train, little reduction gearing Z3 is meshed with the differential mechanism final gear Z4 being arranged on differential casing formation second
Level reducing gear train；Differential mechanism connects wheel by car load semiaxis, and the power of this actuating device will be exported to car load by differential mechanism
Semiaxis drives vehicle wheel rotation；First sun gear S1 of the first single planetary row is connected with the rotor of small machine EM1 by the 3rd axle, the
Second external toothing R2 of two single planetary rows is connected with the rotor of big motor EM2 by the 4th axle；One end of first brake B1 is even
Being connected on the 3rd axle, one end of second brake B2 is connected on the 4th axle, and one end of the 3rd brake B3 is connected to the first axle
On, the other end of the first brake B1, second brake B2 and the 3rd brake B3 is each attached on gear box casing；3rd axle
Being hollow structure inside with the 4th axle, the first axle passes the 3rd axle and the inside of the 4th axle, arranges between the first axle and power shaft
Have first clutch C0, between power shaft and the 3rd axle, be provided with second clutch C1, power shaft by flywheel vibration absorber FW with
The output shaft of electromotor connects.
Further, when the engine assembly matched with performance, described electromotor, small machine, two-row planetary gear
Mechanism, big motor sequentially coaxially arrange placement, and first order reducing gear train, second level reducing gear train and differential mechanism are arranged in little
Between motor and compound planetary gearing, the power of compound planetary gearing exports by double reduction gearing system through differential
Device is transferred to wheel.Wherein the moment of torsion rotating speed of electromotor to match with the rotating speed moment of torsion of big motor, small machine, just can make whole
Individual systematic function is optimum.
According to prior art, single planetary row the most all includes sun gear, planetary gear, planet carrier and external toothing, planet
Wheel is arranged on planet carrier, and planetary gear is meshed with sun gear and external toothing respectively.Specifically in the present invention, the first single planetary row
In PG1, the annexation between each parts is: the first row star-wheel P1 is arranged in the first row carrier PC1, and the first row star-wheel P1 divides
It is not meshed with the first sun gear S1 and the first external toothing R1；In second single planetary row PG2, the annexation between each parts is:
Second planetary gear P2 is arranged on the second planet carrier PC2, the second planetary gear P2 respectively with the second sun gear S2 and the second external toothing
R2 is meshed.
A kind of hybrid transmissions of the present invention, its power is by the output shaft of compound planetary gearing that is second axle
Export and be tied to differential mechanism via double reduction gearing and be transferred to wheel thus drive vehicle to travel.Between power shaft and the first axle
First clutch C0 is set, between power shaft and the 3rd axle, is provided with second clutch C1.When first clutch C0 closes,
Actuating device uses dynamic branch drive pattern；When second clutch C1 and the 3rd brake B3 closes, electromotor and little electricity
Machine is coaxial, and actuating device uses fixed drive ratio drive pattern.3rd axle arranges the first brake B1, drives at hybrid power
Under dynamic model formula during high speed, small machine EM1 will operate near zero-turn speed, and work efficiency is poor, close the first brake B1 locking
Small machine EM1, is maintained the balance of compound planetary gearing, thus avoids little electricity by the friction torque of the first brake B1
Machine EM1 is operated in inefficient interval, is conducive to improving the transmission efficiency of actuating device.4th axle arranges second brake
B2, when automobile travels with hybrid power drive pattern, when vehicle needs high pulling torque to export, can close second clutch C1 and
Two brake B2, electromotor ICE and small machine EM1 Driven by Coaxial, actuating device uses fixed drive ratio drive pattern, the second system
Dynamic device B2 Guan Bi provides the balance fulcrum of compound planetary gearing, can meet the output requirement of car load high pulling torque.
A kind of hybrid transmissions of the present invention, the small machine EM1 in the bi-motor of employing acts primarily as generating effect
With start the function of electromotor, and big motor EM2 acts primarily as driving effect, and the dynamic coupling device used is for by the first single file
Star row and the compound planetary gearing of the second single planetary row composition placed side by side, the first single planetary row and the second single planetary row it
Between gear ratio arrange and restricted the most each other, structure design is more flexible, and the simple in construction of single planetary row is more beneficial for dropping simultaneously
Low gear transmission noises.The present invention, by the accurate control to small machine EM1 and big motor EM2, makes electromotor be in height all the time
Efficiency and the duty of low emission.
A kind of hybrid transmissions of the present invention, the first brake B1, second brake B2, the 3rd brake B3,
First clutch C0 and second clutch C1 is common wet type shifting element.When automobile travels with electric-only mode, first
Clutch C0 and second clutch C1 opens simultaneously and is departed from by electromotor, can control the first brake B1, second brake respectively
B2, the Guan Bi of the 3rd brake B3 realize the pure electric Drive Mode of three fixing gears.When closing second brake B2,
Small machine EM1 is operated alone, it is possible to achieve the first pure electric Drive Mode of gear；When closing the 3rd brake B3, small machine
EM1 and big motor EM2 simultaneously drives, it is possible to achieve the second pure electric Drive Mode of gear；When closing the first brake B1, greatly
Motor EM2 is operated alone, it is possible to achieve the pure electric Drive Mode in third gear position.At the first brake B1, second brake B2 and
When 3rd brake B3 all opens, small machine EM1 and big motor EM2 exports positive-torque simultaneously and drives vehicle, works as small machine
EM1, big motor EM2 rotating speed equal time, planet row each element rotating speed is the most equal, now can obtain high speed without causing
Motor speed is too high.
When automobile travels with hybrid power drive pattern, first clutch C0 closes, and now electromotor ICE is by input
Axle and the first axle connect, and electromotor drives with composite power shunt mode, it is achieved engine speed decouples with speed, starts function
Enough continuous firings are between high efficient area, and control to realize the stepless change of car load by the rotating speed of big motor, small machine
Speed, i.e. E-CVT function, this is also dynamic branch system obvious scheme advantage.
A kind of hybrid transmissions of the present invention, compared with prior art, has the advantage that
1., when automobile travels with electric-only mode, the pure electric Drive Mode of four gears can be realized, it is possible to meet pure
The speed of motorized motions and torque demand, can realize big motor, the optimal control of two motors of small machine simultaneously.
2., when automobile travels with hybrid mode, actuating device mainly uses dynamic branch drive pattern, has simultaneously
Having the hybrid power drive pattern of two fixed drive ratio, mode of operation is flexible, high to the adaptability of road conditions, it is possible to take into account simultaneously
The use demand of car load fuel economy and dynamic property.When first clutch C0 uses Closed type, this actuating device can be very
It is applied to well be driven to main deep hybrid power platform with electromotor；When first clutch C0 uses normally opened type, permissible
It is applied to more stress the plug-in hybrid platform of pure motor driving ability.The technical scheme of this actuating device is a hardware and software platform
Transmission scheme, it is simple to exploitation extensibility product, formed seriation.
Accompanying drawing explanation
The overall structure schematic diagram of Fig. 1: hybrid transmissions
The equivalent lever figure of the Fig. 2 (a): the first pure electric Drive Mode of gear
The equivalent lever figure of the Fig. 2 (b): the second pure electric Drive Mode of gear
Fig. 2 (c): the equivalent lever figure of the pure electric Drive Mode in third gear position
Fig. 2 (d): the equivalent lever figure of the pure electric Drive Mode in fourth gear position
Fig. 3: the equivalent lever figure of pure electronic reversing mode
The equivalent lever figure of the Fig. 4 (a): the first gear hybrid power drive pattern
The equivalent lever figure of the Fig. 4 (b): the second gear hybrid power drive pattern
Fig. 4 (c): the equivalent lever figure of third gear position hybrid power drive pattern
The equivalent lever figure of Fig. 5: hybrid power reversing mode
Detailed description of the invention
Below in conjunction with embodiment, the invention will be further described, but the invention is not limited in the statement of embodiment.
Embodiment 1
A kind of hybrid transmissions, as it is shown in figure 1, include small machine EM1, big motor EM2, differential mechanism 1, power shaft
2, the first single planetary row PG1, the second single planetary row PG2, the first brake B1, second brake B2, the 3rd brake B3, first
Reduction gearing Z1, big retarding gear Z2 and little reduction gearing Z3, first clutch C0, second clutch C1 in the present embodiment are
Normally opened type wet clutch；First single planetary row PG1 includes the first sun gear S1, the first row star-wheel P1, the first row carrier PC1
It is arranged in the first row carrier PC1 with the first external toothing R1, the first row star-wheel P1, the first row star-wheel P1 respectively with the first sun gear
S1 and the first external toothing R1 is meshed；Second single planetary row PG2 includes the second sun gear S2, the second planetary gear P2, the second planet
Frame PC2 and the second external toothing R2, the second planetary gear P2 are arranged on the second planet carrier PC2, the second planetary gear P2 respectively with the second
Sun gear S2 and the second external toothing R2 is meshed；First single planetary row PG1 and the second single planetary row PG2 composition placed side by side are double
Planetary gears 3, the first row carrier PC1 of the first single planetary row PG1 and the second sun gear S2 phase of the second single planetary row PG2
Connect and compose the first axle 4, the second planet carrier PC2 of the first external toothing R1 and the second single planetary row PG2 of the first single planetary row PG1
Being connected to form the second axle 5, the second axle 5 is as the output shaft of compound planetary gearing 3；Second axle 5 is installed first subtract
Speed gear Z1, big retarding gear Z2 are connected by rotating shaft 6 with little reduction gearing Z3, the first reduction gearing Z1 and big retarding gear
Z2 is meshed and forms first order reducing gear train 7, little reduction gearing Z3 and the main deceleration of differential mechanism being arranged on differential mechanism 1 housing
Gear Z4 is meshed and forms second level reducing gear train 8；Differential mechanism 1 connects wheel 10 by car load semiaxis 9, this actuating device
Power will be driven vehicle wheel rotation by differential mechanism output to car load semiaxis；The first sun gear S1 of the first single planetary row PG1 is by the
Three axles 11 are connected with the rotor 12 of small machine EM1, and the second external toothing R2 of the second single planetary row PG2 is by the 4th axle 13 and big electricity
The rotor 14 of machine EM2 connects；One end of first brake B1 is connected on the 3rd axle 11, and one end of second brake B2 is connected to
On 4th axle 13, one end of the 3rd brake B3 is connected on the first axle 4, the first brake B1, second brake B2 and the 3rd
The other end of brake B3 is each attached on gear box casing 15；3rd axle 11 and the 4th axle 13 are hollow structure inside, first
Axle 4, through the 3rd axle 11 and the inside of the 4th axle 13, is provided with first clutch C0, power shaft between the first axle 4 and power shaft 2
2 and the 3rd are provided with second clutch C1 between axle 11, and power shaft 2 is by the output shaft of flywheel vibration absorber FW and electromotor ICE
Connect.During the engine assembly that the actuating device of the present embodiment and performance match, electromotor ICE, small machine EM1, double row
Star gear mechanism 3, big motor EM2 sequentially coaxially arrange placement, first order reducing gear train 7, second level reducing gear train 8 and poor
Speed device 1 is arranged between small machine EM1 and compound planetary gearing 3.
The dynamic coupling device that the present invention uses is to be constituted by the first single planetary row and the second single planetary row are placed side by side
Compound planetary gearing, transmits after the torque coupling that electromotor ICE, small machine EM1, tri-power sources of big motor EM2 input
To reduction gearing, and it is delivered to wheel by differential mechanism through car load semiaxis.Vehicle is during actual travel, and each power source is with each
Shifting element (clutch, brake) is applied in combination and will produce multiple different mode of operation.Electronic will drive automobile is pure below
Work process under dynamic and hybrid power drives is described.
Under pure electric Drive Mode, this actuating device can realize four kinds of mode of operations, and the respectively first gear is pure electronic
Drive pattern EV-1, the second gear pure electric Drive Mode EV-2, third gear position pure electric Drive Mode EV-3, fourth gear position are pure
Electric Drive Mode EV-4, the control planning between each mode of operation and shifting element is as shown in table 1, wherein represents and opens shape
State, ● represent closure state.
Control planning between each mode of operation of table 1 actuating device and shifting element
| Mode of operation | B1 | B2 | B3 | C0 | C1 |
| EV-1 | 〇 | ● | 〇 | 〇 | 〇 |
| EV-2 | 〇 | 〇 | ● | 〇 | 〇 |
| EV-3 | ● | 〇 | 〇 | 〇 | 〇 |
| EV-4 | 〇 | 〇 | 〇 | 〇 | 〇 |
When second brake B2 closes, using small machine EM1 that vehicle is operated alone, this pattern definition is that the first gear is pure
Electric Drive Mode EV-1, this pattern is the high pulling torque output mode of pure motoring condition, the first pure electric Drive Mode of gear
Shown in equivalent lever figure such as Fig. 2 (a), T in figureEM1Represent the moment of torsion of small machine EM1, TLRepresent the vehicle being delivered on the second axle
Running resistance, in figure, arrow represents the moment of torsion on each axle, upwards represents positive-torque, represents downwards negative torque.This pattern underdrive
The gear ratio of device, i.e. small machine EM1 to the gear ratio of vehicle wheel side be:
Wherein, iEV-1It is the gear ratio of the first gear pure electric Drive Mode underdrive device, i1It it is the first single planetary row
The gear ratio (ratio of the numerical value number of teeth equal to the first external toothing R1 and the first sun gear S1, numerical value is negative) of PG1, i2It it is the second list
The gear ratio (ratio of the numerical value number of teeth equal to the second external toothing R2 and the second sun gear S2, numerical value is negative) of planet row PG2, iFDFor
The speed reducing ratio that double reduction gearing is total.Such as select gear ratio and base ratio that planetary design is conventional, it may be assumed that the first single file
The gear ratio i of star row PG11=-2.6, the gear ratio i of the second single planetary row PG22=-1.6, the speed reducing ratio that double reduction gearing is total
iFD=4, data are substituted in above-mentioned formula the gear ratio i being calculated the first gear electric-only mode underdrive deviceEV-1For
28, i.e. when small machine output moment of torsion is 100Nm, wheel will obtain the driving torque of 2800Nm.
When the 3rd brake B3 Guan Bi, using small machine EM1 and big motor EM2 to simultaneously drive, small machine EM1 bears rotating speed
Output negative torque, big motor EM2 positive rotating speed output positive-torque, this pattern definition is the second gear pure electric Drive Mode EV-2,
Shown in equivalent lever figure such as Fig. 2 (b) of the second pure electric Drive Mode of gear, T in figureEM1Represent the moment of torsion of small machine EM1, TEM2
Represent the moment of torsion of big motor EM2, TLRepresenting the vehicle travel resistance being delivered on the second axle, in figure, arrow represents the torsion on each axle
Square, upwards represents positive-torque, represents downwards negative torque.Under this gear, small machine EM1 and big motor EM2 is to the transmission score on wheel limit
It is not:
iEV-2_EM1=-i1*iFD
Wherein, iEV-2_EM1It is the gear ratio of small machine EM1, i under the second pure electric Drive Mode of gearEV-2_EM2It is second
The gear ratio of big motor EM2, i under the pure electric Drive Mode of gear1It is that (numerical value is equal to for the gear ratio of the first single planetary row PG1
The ratio of the number of teeth of one external toothing R1 and the first sun gear S1, numerical value is negative), i2It is the gear ratio (numerical value of the second single planetary row PG2
Equal to the second external toothing R2 and the ratio of the number of teeth of the second sun gear S2, numerical value is negative), iFDFor the deceleration that double reduction gearing is total
Ratio.
When the first brake B1 Guan Bi, using big motor EM2 to be operated alone, this pattern definition is that third gear position is pure electronic
Drive pattern EV-3, this pattern can obtain higher speed.Equivalent lever figure such as Fig. 2 of the pure electric Drive Mode in third gear position
Shown in (c), T in figureEM2Represent the moment of torsion of big motor EM2, TLRepresent the vehicle travel resistance being delivered on the second axle, arrow in figure
Head represents the moment of torsion on each axle, upwards represents positive-torque, represents downwards negative torque.The gear ratio of this gear underdrive device, i.e.
Big motor EM2 to the gear ratio on wheel limit is:
Wherein, iEV-3_EM2For the gear ratio of third gear position pure electric Drive Mode underdrive device, i1It it is the first single file star
The gear ratio (ratio of the numerical value number of teeth equal to the first external toothing R1 and the first sun gear S1, numerical value is negative) of row PG1, i2It is second
The gear ratio (ratio of the numerical value number of teeth equal to the second external toothing R2 and the second sun gear S2, numerical value is negative) of single planetary row PG2, iFD
For the speed reducing ratio that double reduction gearing is total.
Along with speed increases further, under above-mentioned each gear small machine EM1, big two motors of motor EM2 rotating speed all
The most too high, now the first brake B1, second brake B2 and the 3rd all open modes of brake B3, use little electricity
Machine EM1 and big motor EM2 simultaneously drives, and this pattern definition is fourth gear position pure electric drive mode EV-4, and fourth gear position is pure electronic
Shown in equivalent lever figure such as Fig. 2 (d) of drive pattern, T in figureEM1Represent the moment of torsion of small machine EM1, TEM2Represent big motor EM2
Moment of torsion, TLRepresenting the vehicle travel resistance being delivered on the second axle, in figure, arrow represents the moment of torsion on each axle, is just upwards representing
Moment of torsion, represents downwards negative torque.This pattern lower whorl limit obtains driving torque:
TwheelEV-4=(TEM1+TEM2)*iFD
Wherein, TwheelEV‐4Driving torque, T is obtained for pure electric Drive Mode lower whorl limit, fourth gear positionEM1For small machine
The moment of torsion of EM1, TEM2For the moment of torsion of big motor EM2, iFDFor the speed reducing ratio that double reduction gearing is total.When small machine EM1, big motor
When EM2 rotating speed is equal, each planetary gear elements rotating speed is the most equal, and now vehicle can obtain max. speed without causing small machine
EM1, two motor self rotating speeds of big motor EM2 are too high.
When pure electronic reversing, use the first gear pure electric Drive Mode EV-1, control small machine EM1 and bear rotating speed output
Negative torque, the equivalent lever figure of pure electronic reversing mode is as it is shown on figure 3, T in figureEM1Represent the moment of torsion of small machine EM1, TLRepresent
Being delivered to the vehicle travel resistance on the second axle, in figure, arrow represents the moment of torsion on each axle, upwards represents positive-torque, represents downwards
Negative torque.
Under hybrid power drive pattern, this actuating device can realize four kinds of mode of operations, the respectively first gear mixing
Power drive mode HEV-1, the second gear hybrid power drive pattern HEV-2, third gear position hybrid power drive pattern HEV-
3, hybrid power reversing mode, the control planning between each mode of operation and shifting element is as shown in table 2, wherein represents and opens
State, ● represent closure state.
Control planning between each mode of operation of table 2 actuating device and shifting element
| Mode of operation | B1 | B2 | B3 | C0 | C1 |
| HEV-1 | 〇 | ● | 〇 | 〇 | ● |
| HEV-2 | 〇 | 〇 | 〇 | ● | 〇 |
| HEV-3 | ● | 〇 | 〇 | ● | 〇 |
| Hybrid power reversing mode | 〇 | 〇 | ● | 〇 | ● |
When the first gear hybrid power drive pattern HEV-1, second brake B2 and second clutch C1 Guan Bi, now
Electromotor ICE and small machine EM1 Driven by Coaxial, it is achieved high pulling torque exports, the equivalent thick stick of the first gear hybrid power drive pattern
Shown in bar figure such as Fig. 4 (a), T in figureEM1Represent the moment of torsion of small machine EM1, TICERepresent the moment of torsion of electromotor ICE, TLRepresent transmission
Vehicle travel resistance on the second axle, in figure, arrow represents the moment of torsion on each axle, upwards represents positive-torque, represents downwards negative twist
Square.The fixed drive ratio of this pattern is identical with the fixed drive ratio of the first gear pure electric Drive Mode EV-1, uses first gear
Position pure electric Drive Mode torque arithmetic time gear ratio value, when electromotor ICE and small machine EM1 exports 150Nm jointly
Time, the driving torque that wheel can obtain is 4200Nm.
When second brake B2 opens, big motor EM2 participates in work, is now defined as the second gear hybrid power and drives
Pattern HEV-2 i.e. dynamic branch pattern.This pattern is as the main hybrid power drive pattern of whole actuating device, it is possible to realize
Car load infinitely variable speeds E-CVT function, shown in equivalent lever figure such as Fig. 4 (b) of the second gear hybrid power drive pattern, in figure
TEM1Represent the moment of torsion of small machine EM1, TEM2Represent the moment of torsion of big motor EM2, TICERepresent the moment of torsion of electromotor ICE, TLRepresent and pass
Being delivered to the vehicle travel resistance on the second axle, in figure, arrow represents the moment of torsion on each axle, upwards represents positive-torque, represents downwards negative
Moment of torsion.This pattern is stepless shift mode, does not has fixed drive ratio.When sliding with Brake energy recovery occurs in vehicle, first
Clutch C0 opens and disconnects electromotor ICE more effectively to reclaim braking energy.This pattern can be used for astern condition.
When vehicle speed is higher, small machine EM1 can operate near zero-turn speed, now small machine poor efficiency, controls
First brake B1 closes small machine EM1 locking, is conducive to improving the transmission efficiency of this operating mode underdrive device.This fixing biography
Dynamic is third gear position hybrid power drive pattern HEV-3 than pattern definition, third gear position hybrid power drive pattern HEV-3 etc.
Shown in effect lever diagram such as Fig. 4 (c), T in figureEM2Represent the moment of torsion of big motor EM2, TICERepresent the moment of torsion of electromotor ICE, TLRepresent
Being delivered to the vehicle travel resistance on the second axle, in figure, arrow represents the moment of torsion on each axle, upwards represents positive-torque, represents downwards
Negative torque.The moment of torsion that this pattern lower whorl limit obtains includes from electromotor ICE and big motor EM2 moment of torsion sum, such as following formula
Shown in:
Wherein, TwheelHEV‐3Driving torque, T is obtained for hybrid power drive pattern lower whorl limit, third gear positionICEFor starting
The moment of torsion of machine ICE, TEM2For the moment of torsion of big motor EM2, i1Be the first single planetary row PG1 gear ratio (numerical value be equal to the first external tooth
The ratio of the number of teeth of circle R1 and the first sun gear S1, numerical value is negative), i2It is that (numerical value is equal to for the gear ratio of the second single planetary row PG2
The ratio of the number of teeth of two external toothing R2 and the second sun gear S2, numerical value is negative), iFDFor the speed reducing ratio that double reduction gearing is total.
Prioritizing selection pure electronic reversing mode during vehicle backing, uses hybrid power reversing mode when the batteries are low,
Now Guan Bi the 3rd brake B3 and second clutch C1, the equivalent lever figure of hybrid power reversing mode is as shown in Figure 5.Now
The driving torque that wheel limit obtains is:
TwheelHEV-reverse=(TICE+TEM1)*(-i1)*iFD
Wherein, TwheelHEV‐reverseDriving torque, T is obtained for hybrid power reversing mode lower whorl limitICEFor electromotor ICE
Moment of torsion, TEM1For the moment of torsion of small machine EM1, i1Be the first single planetary row PG1 gear ratio (numerical value be equal to the first external toothing R1
With the ratio of the number of teeth of the first sun gear S1, numerical value is negative), iFDFor the speed reducing ratio that double reduction gearing is total.
Claims (3)
1. a hybrid transmissions, including small machine (EM1), big motor (EM2), differential mechanism, power shaft, its feature exists
In: also include the first single planetary row (PG1), the second single planetary row (PG2), the first brake (B1), second brake (B2),
Three brakes (B3), the first reduction gearing (Z1), big retarding gear (Z2) and little reduction gearing (Z3), the first single planetary row
(PG1) including the first sun gear (S1), the first row star-wheel (P1), the first row carrier (PC1) and the first external toothing (R1), second is single
Planet row (PG2) includes the second sun gear (S2), the second planetary gear (P2), the second planet carrier (PC2) and the second external toothing (R2),
First single planetary row (PG1) and the second single planetary row (PG2) composition placed side by side compound planetary gearing, the first single planetary row
Second sun gear (S2) of the first row carrier (PC1) and the second single planetary row be connected to form the first axle, the first single planetary row
Second planet carrier (PC2) of the first external toothing (R1) and described second single planetary row be connected to form the second axle, at the second axle
Upper installation the first reduction gearing (Z1), big retarding gear (Z2) is connected by rotating shaft with little reduction gearing (Z3), and first slows down
Gear (Z1) be meshed with big retarding gear (Z2) formation first order reducing gear train, little reduction gearing (Z3) be arranged on differential
Differential mechanism final gear (Z4) on device housing is meshed and forms second level reducing gear train；Differential mechanism is by car load semiaxis even
Picking up wheel, the power of this actuating device will be driven vehicle wheel rotation by differential mechanism output to car load semiaxis；The of first single planetary row
One sun gear (S1) is connected with the rotor of small machine (EM1) by the 3rd axle, and second external toothing (R2) of the second single planetary row leads to
Cross the 4th axle to be connected with the rotor of big motor (EM2)；One end of first brake (B1) is connected on the 3rd axle, second brake
(B2) one end is connected on the 4th axle, and one end of the 3rd brake (B3) is connected on the first axle, the first brake (B1),
The other end of two brakes (B2) and the 3rd brake (B3) is each attached on gear box casing；3rd axle and the 4th axle are internal
Hollow structure, the first axle passes the 3rd axle and the inside of the 4th axle, is provided with first clutch between the first axle and power shaft
(C0), being provided with second clutch (C1) between power shaft and the 3rd axle, power shaft passes through flywheel vibration absorber (FW) and electromotor
Output shaft connect.
2. a kind of hybrid transmissions as claimed in claim 1, it is characterised in that: at the electromotor matched with performance
During assembling, described electromotor, small machine, compound planetary gearing, big motor sequentially coaxially arrange placement, first order reducing gear
Train, second level reducing gear train and differential mechanism are arranged between small machine and compound planetary gearing.
3. a kind of hybrid transmissions as claimed in claim 1 or 2, it is characterised in that: when first clutch (C0) closes
During conjunction, actuating device uses dynamic branch drive pattern；When second clutch (C1) and the 3rd brake (B3) close, start
Machine is coaxial with small machine, and actuating device uses fixed drive ratio drive pattern.
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| CN109203972A (en) * | 2018-11-14 | 2019-01-15 | 上海汉老汽车科技有限公司 | A kind of double-motor hybrid power system transmission device |
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| WO2020024596A1 (en) * | 2018-08-02 | 2020-02-06 | 宁波上中下自动变速器有限公司 | Power system for hybrid vehicle |
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| CN112590525A (en) * | 2020-12-16 | 2021-04-02 | 浙江盘毂动力科技有限公司 | Dual-motor driven electromechanical hybrid transmission stepped speed change structure and vehicle |
| CN113232502A (en) * | 2021-06-21 | 2021-08-10 | 上海爱跻企业管理咨询合伙企业(有限合伙) | Hybrid vehicle driving system and vehicle |
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| CN113400919A (en) * | 2021-06-21 | 2021-09-17 | 上海爱跻企业管理咨询合伙企业(有限合伙) | Multi-mode power split hybrid electric vehicle driving system and vehicle |
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