CN111412253B - Automatic gear shifting transmission without cutting off power - Google Patents
Automatic gear shifting transmission without cutting off power Download PDFInfo
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- CN111412253B CN111412253B CN202010286535.5A CN202010286535A CN111412253B CN 111412253 B CN111412253 B CN 111412253B CN 202010286535 A CN202010286535 A CN 202010286535A CN 111412253 B CN111412253 B CN 111412253B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0078—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratio comprising twelve or more forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
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Abstract
The invention discloses a non-cutoff power shifting automatic transmission, which relates to the field of new energy automobile automatic transmissions and comprises an input shaft, a transmission shaft, a first planetary gear mechanism, a second planetary gear mechanism, a first motor and a second motor; the input shaft and the transmission shaft respectively rotate synchronously with a gear ring and a sun gear of the first planetary gear mechanism; the planet carrier of the first planetary gear mechanism drives the planet carrier of the second planetary gear mechanism to synchronously rotate; a clutch is arranged between the planet carrier of the first planetary gear mechanism and the transmission shaft; the sun gear of the second planetary gear mechanism is fixedly connected with the rotor of the first motor, the transmission shaft is fixedly connected with the rotor of the second motor, and the stator of the first motor and the stator of the second motor are fixedly connected with the gear ring of the second planetary gear. The transmission efficiency is high, the transmission torque is large, the gear shifting is smooth and free from impact, and the energy recovery can be realized.
Description
Technical Field
The invention relates to the field of automatic transmissions of new energy automobiles, in particular to a power-uninterrupted gear-shifting automatic transmission.
Background
AT present, five kinds of transmissions of CVT, DSG, AT, AMT and hybrid-driven ECVT exist in the automatic transmission of the automobile.
The CVT automatic transmission has the advantages that the transmission efficiency is high, the speed change is smooth and flexible, no power interruption is caused during the speed change, the rotating speed of an engine is not required to be suddenly changed during the gear change, the torque is changed, the gear change is continuous, the requirement on an output torque curve of the engine is not strict, and the acceleration performance of a vehicle is good; but the transmission torque is smaller, the speed ratio range of the transmission is smaller, and the failure rate is high.
The DCT automatic transmission has high transmission efficiency, short theoretical gear shifting time, large transmission torque, small gear shifting impact and good acceleration performance of a vehicle; however, when the gear is shifted, the engine is required to change the rotating speed, pause or reduce the output torque of the engine, and the output torque curve of the engine is required to be smooth. In recent years, DCT automatic transmissions generally have a phenomenon of starting jerking and shifting jerking in use of compact cars, and have a large impact on a transmission system, and the main reason is that, in the shift time control and the friction coefficient of a clutch, although the jerking phenomenon can be alleviated by extending the half-engagement time of the clutch, the shift time is increased, the wear of the clutch is aggravated, the temperature of the clutch is increased, and the shift jerking feeling is enhanced.
The AT automatic transmission is the most widely applied automatic transmission AT present, and has the advantages of low transmission efficiency, short gear shifting time, large transmission torque and small gear shifting impact; but the structure is complex, the production cost is high, the failure rate of the control oil way is high, and the requirement on the lubricating oil of the transmission is higher. The AT automatic transmission requires the engine to change the rotation speed, suspend or reduce the output torque of the engine when shifting gears, and requires the output torque curve of the engine to be smooth.
The AMT realizes the automatic gear shifting by additionally arranging a TCU speed change control system on the basis of a manual transmission, and has low cost, high transmission efficiency and large transmission torque; however, the gear shifting time is long, the engine is required to change the rotating speed during gear shifting, the output torque of the engine is suspended or reduced, and the output torque curve of the engine is required to be smooth. The AMT automatic transmission is particularly strong in jerk, poor in driving comfort, and poor in vehicle acceleration performance at the time of gear shifting.
The CVT, DCT, AT and AMT transmissions described above do not achieve regenerative and retarding functions of braking energy.
The ECVT automatic transmission mainly comprises a No. 1 motor, a No. 2 motor and a planetary gear set, wherein in the power transmission process, input power is divided into two paths of power transmission through a planetary gear, one path of power is output through a gear ring of the planetary gear, the other path of power is transmitted to the No. 1 motor through a sun gear of the planetary gear, the No. 1 motor freely rotates to work in a power generation mode, kinetic energy is converted into electric energy, then the electric energy is converted into the kinetic energy through the No. 2 motor, and the kinetic energy and the power output by the gear ring of the planetary gear drive the vehicle to run together. The ECVT automatic transmission has the advantages that the theoretical speed ratio range is large, the speed change is smooth and flexible, no power interruption is caused during the speed change, the sudden change of the rotating speed of an engine and the change of torque are not required during the gear change, the gear change is continuous, and the requirement on the output torque curve of the engine is not strict; but the transmission efficiency is lower, the low-gear output torque is smaller, and the energy loss is larger in the energy conversion process.
In the prior art, the various automatic transmissions are mostly used for small vehicles due to the reasons of small transmission torque, large transmission impact, long gear shifting time, complex control and the like, while large vehicles such as trucks and the like can only rely on manual transmissions to realize speed change, the large vehicles are limited by the engine speed, and require rapid response and operation of drivers during speed change, so that the large vehicles have higher requirements on the driving skills of the drivers.
In addition, as fossil energy is gradually exhausted, traditional automobiles powered by petroleum energy are gradually eliminated, and energy-saving and environment-friendly new energy automobiles become the development trend of the industry. At present, the development bottleneck of new energy automobiles is mainly reflected in the insufficient cruising ability of the new energy automobiles, more energy waste is actually generated in the processes of gear shifting, speed changing, braking and the like of the automobiles, and the waste energy is recycled, so that the new energy automobiles have important significance in improving the cruising ability of the new energy automobiles and promoting the industrial development of the new energy automobiles.
Disclosure of Invention
The invention aims to overcome the defects of the prior art, and provides a non-cut-off power shifting automatic transmission which has high transmission efficiency, large transmission torque, smooth shifting and no impact, improves the driving comfort of automobiles, can be applied to automatic speed change of large commercial vehicles such as heavy-duty trucks and the like, and can also be applied to small passenger vehicles; meanwhile, the energy recovery can be realized, and the important significance for promoting the development of new energy automobile industry is achieved.
The purpose of the invention is realized by the following technical scheme:
a non-cutting-off power shifting automatic transmission is characterized by comprising an input shaft, a transmission shaft, a first planetary gear mechanism, a second planetary gear mechanism, a first motor and a second motor;
the input shaft is used for driving the gear ring of the first planetary gear mechanism to rotate, and the sun gear of the first planetary gear mechanism is used for driving the transmission shaft to rotate;
the planet carrier of the first planetary gear mechanism is used for driving the planet carrier of the second planetary gear mechanism to synchronously rotate;
the sun gear of the second planetary gear mechanism is fixedly connected with the rotor of the first motor, the transmission shaft is connected with the rotor of the second motor, and the stator of the first motor and the stator of the second motor are fixedly connected with the gear ring of the second planetary gear.
Furthermore, the planetary gear set further comprises a clutch, and the clutch is used for realizing disconnection or driving connection of the planet carrier of the first planetary gear mechanism and the transmission shaft.
Further, the device also comprises a hollow shaft a and a hollow shaft b;
the transmission shaft, the hollow shaft a, the hollow shaft b, the sun gear of the first planetary gear mechanism and the sun gear of the second planetary gear mechanism are all arranged concentrically;
the sun gear of the first planetary gear mechanism is fixedly sleeved on the transmission shaft, and two ends of the hollow shaft a are respectively and fixedly connected with the planet carrier of the first planetary gear mechanism and the planet carrier of the second planetary gear mechanism;
the hollow shaft b is rotatably sleeved on the transmission shaft, and the sun gear of the second planetary gear mechanism and the rotor of the first motor are fixedly sleeved on the hollow shaft b.
Further, the device also comprises a flange a and a motor base;
one end of the input shaft is fixedly connected with the gear ring of the first planetary gear mechanism through a flange a;
the motor cabinet is hollow structure, the one end of motor cabinet with second planetary gear's ring gear fixed connection, bayonet motor is all chooseed for use to first motor and second motor, the equal fixed mounting of first motor and second motor is in the motor cabinet.
Further, the hollow shaft further comprises a clutch, and the clutch is arranged in the hollow shaft a; the clutch is used for realizing connection and disconnection of the hollow shaft a and the transmission shaft.
Furthermore, the motor comprises a third planetary gear mechanism and a hollow shaft c, wherein one end of the transmission shaft, which is far away from the flange a, is fixedly connected with a planet carrier of the third planetary gear mechanism, the motor seat is fixedly connected with a gear ring of the third planetary gear mechanism, a sun gear of the third planetary gear mechanism and the hollow shaft c are both arranged concentrically with the transmission shaft, the hollow shaft c is rotatably sleeved on the transmission shaft, and a rotor of the second motor and a sun gear of the third planetary gear mechanism are both fixedly sleeved on the hollow shaft c. .
Further, when applied to an eight-speed transmission of a vehicle such as a large bus, the power-cut-off automatic transmission is configured to:
two intermediate shafts a are symmetrically arranged on two sides of the input shaft, and two intermediate shafts b are symmetrically arranged on two sides of the input shaft;
an input driving gear is fixedly sleeved on the input shaft, input driven gears are fixedly sleeved on the two intermediate shafts a, and the input driving gear is meshed with the input driven gears;
an output driving gear is fixedly sleeved on the hollow shaft a, output driven gears are fixedly sleeved on the two intermediate shafts b, and the output driven gears are meshed with the output driving gear;
two intermediate shafts a are fixedly sleeved with 7-15 gears of driving gears, 5-13 gears of driving gears, 3-11 gears of driving gears and 1-9 gears of driving gears, and further comprise 7-15 gears of driven gears, 5-13 gears of driven gears, 3-11 gears of driven gears and 1-9 gears of driven gears, two 7-15 gears of driving gears are meshed with 7-15 gears of driven gears, two 5-13 gears of driving gears are meshed with 5-13 gears of driven gears, two 3-11 gears of driving gears are meshed with 3-11 gears of driven gears, and two 1-9 gears of driving gears are meshed with 1-9 gears of driven gears;
2-4-10-12 gear driving gears, 6-8-14-16 gear driving gears and reverse gear driving gears are fixedly sleeved on the two intermediate shafts b, and the two intermediate shafts b further comprise 2-4-10-12 gear driven gears, 6-8-14-16 gear driven gears, reverse gear driven gears and two reverse gear intermediate gears, the two 2-4-10-12 gear driving gears are meshed with the 2-4-10-12 gear driven gears, the two 6-8-14-16 gear driving gears are meshed with the 6-8-14-16 gear driven gears, and the two reverse gear driving gears are in transmission connection with the reverse gear driven gears through the two reverse gear intermediate gears respectively;
the gear coupling sleeve comprises a gear coupling sleeve a, a gear coupling sleeve b, a gear coupling sleeve c and a gear coupling sleeve 1; the gear coupling sleeve a is used for connecting or disconnecting the 2-4-10-12 driven gear with or from the secondary shaft and for connecting or disconnecting the 6-8-14-16 driven gear with or from the secondary shaft, the gear coupling sleeve b is used for connecting or disconnecting the reverse driven gear with or from the secondary shaft and for connecting or disconnecting the 7-15 driven gear with or from the secondary shaft, the gear coupling sleeve c is used for connecting or disconnecting the 5-13 driven gear with or from the secondary shaft and for connecting or disconnecting the 3-11 driven gear with or from the secondary shaft, and the 1-gear coupling sleeve is used for connecting or disconnecting the 1-9 driven gear with or from the secondary shaft;
the gear shifting mechanism further comprises a P-gear, and the P-gear is fixedly connected with the second shaft.
Further, when the automatic transmission is applied to sixteen-speed change of large-sized vehicles such as heavy-duty trucks and the like, the automatic transmission comprises a power output shaft, an auxiliary box planetary gear mechanism and a high-low gear combination sleeve on the basis of the eight-speed change, wherein the power output shaft is fixedly connected with a planet carrier of the auxiliary box planetary gear mechanism, a sun gear of the auxiliary box planetary gear mechanism is fixedly sleeved on the secondary shaft, the 1-gear combination sleeve is replaced by a 1-9 gear combination sleeve, the 1-9 gear combination sleeve is used for connecting or disconnecting the 1-9 gear driven gear with the secondary shaft, or the 1-9 gear combination sleeve is used for connecting or disconnecting the 1-9 gear driven gear with the planet carrier of the auxiliary box planetary gear mechanism, and the high-low gear combination sleeve is used for connecting a gear ring of the auxiliary box planetary gear mechanism with the planet carrier of the auxiliary box planetary gear mechanism, or for connecting a ring gear of the auxiliary box planetary gear mechanism with a transmission housing;
the P gear is fixedly connected with the two shafts and is not directly fixed on a planet carrier of the auxiliary box planetary gear mechanism.
Further, when the automatic transmission is applied to the transverse eight-speed change of a car, the automatic transmission comprises a shell, wherein a transmission shaft a, a hollow shaft d, a hollow shaft e, a Ravigneaux planetary gear mechanism and a single-row two-stage planetary gear mechanism are arranged in the shell;
the transmission shaft a, the hollow shaft d and the hollow shaft e are arranged concentrically, the transmission shaft a penetrates through the hollow shaft d, and the hollow shaft d penetrates through the hollow shaft e;
one end of the transmission shaft a is fixedly sleeved with a driven main gear, the input shaft is fixedly sleeved with a driving main gear, the driven main gear is meshed with the driving main gear, the other end of the transmission shaft a is fixedly connected with a sun gear of the single-row double-stage planetary gear mechanism, and a planet carrier of the single-row double-stage planetary gear mechanism is fixedly connected with the shell;
the hollow shaft d is fixedly connected with a sun gear of the Ravigneaux type planetary gear mechanism, an outer gear is sleeved outside a gear ring of the Ravigneaux type planetary gear mechanism, an output driving gear is fixedly sleeved on the hollow shaft a, and the outer gear is meshed with the output driving gear;
a transmission gear a is fixedly arranged on the hollow shaft e, a transmission gear b is coaxially and fixedly connected to an outer planet wheel of the Ravigneaux type planetary gear mechanism, and the transmission gear a is meshed with the transmission gear b;
the clutch gear shifting device comprises a clutch gear shifting device a, a clutch gear shifting device b, a clutch gear shifting device c, a clutch gear shifting device d and a clutch gear shifting device e;
the clutch gear shifting device a is used for enabling a gear ring of the single-row double-stage planetary gear mechanism to be connected with or disconnected from the hollow shaft d, the clutch gear shifting device b is used for enabling the gear ring of the single-row double-stage planetary gear mechanism to be connected with or disconnected from the hollow shaft e, the clutch gear shifting device c is used for enabling the hollow shaft e to be connected with or disconnected from the shell, the clutch gear shifting device d is used for enabling a planet carrier of the Ravigneaux planetary gear mechanism to be connected with or disconnected from the shell, and the clutch gear shifting device e is used for enabling the planet carrier of the Ravigneaux planetary gear mechanism to be connected with or disconnected from the transmission shaft a.
Furthermore, in order to obtain better transmission speed ratio and effect and be more suitable for vehicles such as cars and the like, the transverse eight-speed variable-speed automatic transmission applied to the cars is additionally provided with a clutch gear shifting device f without a clutch, and the main structure of the transverse eight-speed variable-speed automatic transmission also comprises a shell, wherein a transmission shaft a, a hollow shaft d, a hollow shaft e, a Ravigna type planetary gear mechanism and a single-row two-stage planetary gear mechanism are arranged in the shell;
the transmission shaft a, the hollow shaft d and the hollow shaft e are arranged concentrically, the transmission shaft a penetrates through the hollow shaft d, and the hollow shaft d penetrates through the hollow shaft e;
one end of the transmission shaft a is fixedly sleeved with a driven main gear, the input shaft is fixedly sleeved with a driving main gear (300), the driven main gear is meshed with the driving main gear, the other end of the transmission shaft a is fixedly connected with a sun gear of the single-row double-stage planetary gear mechanism, and a planet carrier of the single-row double-stage planetary gear mechanism is fixedly connected with the shell;
the hollow shaft d is fixedly connected with a sun gear of the Ravigneaux type planetary gear mechanism, an outer gear is sleeved outside a gear ring of the Ravigneaux type planetary gear mechanism, an output driving gear is fixedly sleeved on the hollow shaft a, and the outer gear is meshed with the output driving gear;
a transmission gear a is fixedly arranged on the hollow shaft e, a transmission gear b is coaxially and fixedly connected to an outer planet wheel of the Ravigneaux type planetary gear mechanism, and the transmission gear a is meshed with the transmission gear b;
the clutch gear shifting device comprises a clutch gear shifting device a, a clutch gear shifting device b, a clutch gear shifting device c, a clutch gear shifting device d, a clutch gear shifting device e and a clutch gear shifting device f;
the clutch gear shifting device a is used for enabling a gear ring of the single-row double-stage planetary gear mechanism to be connected or disconnected with the hollow shaft d, the clutch gear shifting device b is used for enabling the gear ring of the single-row double-stage planetary gear mechanism to be connected or disconnected with the hollow shaft e, the clutch gear shifting device c is used for enabling the hollow shaft e to be connected or disconnected with the shell, the clutch gear shifting device d is used for enabling a planet carrier of the Ravigneaux planetary gear mechanism to be connected or disconnected with the shell, the clutch gear shifting device e is used for enabling the planet carrier of the Ravigneaux planetary gear mechanism to be connected or disconnected with the transmission shaft a, and the clutch gear shifting device f is used for enabling the hollow shaft d and the transmission shaft a to be connected or disconnected.
The invention has the beneficial effects that:
the automatic transmission without cutting off power shifting is provided with the core transmission component, the core transmission component is provided with the two motors which can be used as the generator and the motor and the two planetary gear mechanisms, and the automatic transmission can be applied to transmissions with different grade requirements and mainly has the following beneficial effects.
1. And energy recovery is realized. The motor can be used as a motor and a motor, so that the kinetic energy of the vehicle can be converted into electric energy under the conditions of long downhill driving, braking and the like of the vehicle, and the electric energy is stored in the battery to realize the recycling of the energy.
2. The driving safety is improved, in the energy conversion process, the power generation load of the motor is fed back to the vehicle, the vehicle can be decelerated, the speed slowing function is realized, the braking performance is more reliable, and the service life of a braking element is prolonged. When the vehicle runs on a slope, the motor can be used as a motor to provide slope auxiliary torque, so that vehicle sliding is effectively prevented, and driving safety is improved. Especially, the automatic speed change of large vehicles such as heavy-duty trucks and the like can be realized, so that the large vehicles are easy and comfortable to control, and the driving safety is improved
3. The power is not interrupted in the process of speed change and gear shifting. When the automobile starts and shifts gears, electric power can be input to enable the motor to be used as a motor, the output rotating speed of the core transmission component is regulated and controlled to directly reach the rotating speed value required by the gear to be shifted, the corresponding gear is engaged after synchronization, the power of the engine is not cut off, the gear shifting process is smooth and impact-free, the acceleration performance of the automobile is good, the automobile does not have pause feeling during running, the service lives of the transmission and the whole automobile are effectively prolonged, and the driving comfort of the automobile is improved.
4. The transmission has wide application range. The speed changer is used as a motor through a motor, the output rotating speed of the core transmission component is regulated and controlled, and the speed changer is directly enabled to reach the rotating speed value required by the gear to be shifted to realize gear shifting. During the gear shifting process, a series of actions of reducing the output torque of an engine, separating the current gear of a transmission, synchronizing the rotating speed of the engine and the rotating speed of a gear to be shifted into a gearbox, combining the gear and recovering the torque output of the engine are not required to be executed, signals such as the depth of an accelerator pedal, the load of the engine, the water temperature, fault indication, braking and the like are only required to be sent to an engine control module through a CAN bus during control, and then CAN bus data signals are monitored, so that the gear shifting requirement CAN be met, the CAN bus CAN be matched with the engine easily, the engine CAN work in an economic working condition as much as possible, the engine with a poor torque curve and good economy CAN be selected, and the fuel economy of a vehicle is good and the emission is low.
4. The clutch is arranged, so that the transmission is high in transmission efficiency and large in transmission torque when the vehicle runs normally; meanwhile, the transmission is suitable for transmissions with different series requirements and has wide applicability.
5. The gearbox can enable the engine to work under the optimal economic working condition for a long time, so that the fuel economy of the engine is improved; under the best working condition of the engine, the exhaust emission is cleaner.
6. The motor power generation of the gearbox can be used for heating the engine, so that the engine can be warmed as soon as possible, the main abrasion of the engine is concentrated on cold vehicle starting and cold vehicle running, the service life of the engine is prolonged, and the vehicle warming time and fuel required by the engine are saved.
Drawings
FIG. 1 is a schematic illustration of the core transmission components of a non-cutting power shifting automatic transmission of the present invention;
FIG. 2 is a schematic diagram of a core transmission component structure of an automatic transmission without power-off shifting applied to a large vehicle according to the present invention;
fig. 3 is a schematic structural view of embodiment 1 of a non-power-off shifting automatic transmission of the present invention;
FIG. 4 is a schematic structural view of embodiment 2 of a non-power-off shifting automatic transmission of the present invention;
FIG. 5 is a schematic structural view of embodiment 3 of a non-power-off shifting automatic transmission of the present invention;
fig. 6 is a schematic configuration diagram of embodiment 4 of a power-shift-free automatic transmission of the present invention.
Detailed Description
The technical solutions of the present invention are further described in detail below with reference to the accompanying drawings, but the scope of the present invention is not limited to the following.
As shown in fig. 1 and 2, a non-power-off automatic transmission includes a core power transmission member. The core gear assembly includes an input shaft 110, a drive shaft 120, a first planetary gear mechanism, a second planetary gear mechanism, a first electrical machine, and a second electrical machine.
The first planetary gear mechanism and the second planetary gear mechanism are conventional planetary gear mechanism structures in the prior art, and comprise a sun gear, a plurality of planet gears and a gear ring which are arranged from inside to outside, wherein the sun gear and the gear ring are meshed with the planet gears, and the planetary gear mechanism further comprises a planet carrier which is used for mounting the planet gears and enables the relative positions of the planet carriers to be fixed. When the planetary gear mechanism is used, three input or output parts are arranged on the planetary gear mechanism, namely a gear ring, a planet carrier and a sun gear, three rotating shafts can allow power to be input or output, the rotation of one shaft can be limited when needed by means of a clutch or a brake, and the other two shafts are left for transmission, so that the relationship between the gears which are meshed with each other can be in various combinations.
The first motor and the second motor are both motors which can be used as motors and motors in the prior art, and can be selected from three-phase alternating current synchronous motors, direct current brushless motors, reluctance motors and the like, can generate electricity to generate electric energy in an excitation state, and can also be driven by a power grid to operate and output power.
The input shaft 110 is used for driving the ring gear 141 of the first planetary gear mechanism to rotate, and the sun gear 143 of the first planetary gear mechanism is used for driving the transmission shaft 120 to rotate; the planet carrier 142 of the first planetary gear mechanism is used for driving the planet carrier 152 of the second planetary gear mechanism to rotate synchronously; the sun gear 153 of the second planetary gear mechanism is fixedly connected with the rotor 171 of the first motor, the transmission shaft 120 is connected with the rotor 181 of the second motor, and the stator 172 of the first motor and the stator 182 of the second motor are both fixedly connected with the ring gear 151 of the second planetary gear.
Further, the core transmission member may further include a clutch 134, and the clutch 134 is used for realizing disconnection or driving connection of the carrier 142 of the first planetary gear mechanism and the transmission shaft 120.
The carrier 142 of the first planetary gear mechanism and the carrier 152 of the second planetary gear mechanism are connected to other gear sets of the automatic transmission as output means of the core power transmission member, and complete power output. In use, power from the vehicle engine is transmitted to the ring gear 141 of the first planetary gear set via the input shaft 110 and drives it to rotate.
When the clutch 134 connects the carrier 142 of the first planetary gear mechanism to the transmission shaft 120 during normal running of the vehicle, the sun gear 143 of the first planetary gear mechanism is fixed to the carrier 142, and the power transmitted from the input shaft 110 is directly transmitted to the sun gear 143 and the carrier 142 via the ring gear 141 of the first planetary gear mechanism, thereby completing output. When the automobile normally runs, the planet carrier 152 of the second planetary gear mechanism rotates along with the planet carrier 142 of the first planetary gear mechanism, under the action of the second planetary gear mechanism, the ring gear 151 and the sun gear 153 of the second planetary gear mechanism relatively move, the stator 172 and the rotor 171 of the first motor can relatively rotate, the first motor can be in a power generation state, and the generated electric energy is stored in the battery to recover part of energy. Meanwhile, the transmission shaft 120 can drive the rotor 181 of the second motor to rotate, so that the stator 182 and the rotor 181 of the second motor can rotate relatively, the second motor can also be in a power generation state, and the generated electric energy is stored in the battery to realize the recovery of partial energy.
Further, when used in an automatic transmission for a large vehicle, the core transmission may be additionally provided with a third planetary gear mechanism through which the transmission shaft 120 is connected to the rotor 181 of the second motor. Specifically, the transmission shaft 120 is connected to the carrier 162 of the third planetary gear mechanism, and the sun gear 163 of the third planetary gear mechanism is connected to the rotor 181 of the second motor, so that the purpose of increasing the torque can be achieved, and the transmission shaft is suitable for large vehicles. In the process, the first motor and the second motor can input currents with different magnitudes and directions under the control of the system, so that the first motor and the second motor are converted into a motor mode, and the automatic transmission is shifted without cutting off power. When the automobile needs to perform starting, gear shifting and other operations, the clutch 134 enables the planet carrier 142 of the first planetary gear mechanism to be in a disconnected state with the transmission shaft 120, at this time, power input through the input shaft 110 is divided into two paths to flow out under the action of the first planetary gear mechanism, wherein one path is transmitted to the planet carrier 162 of the third planetary gear mechanism through the sun gear 143 of the first planetary gear mechanism and the transmission shaft 120, and then is transmitted to the rotor 181 of the second motor through the sun gear 163 of the third planetary gear mechanism; the other path drives the carrier 142 of the first planetary gear mechanism and the carrier 152 of the second planetary gear mechanism to rotate, and due to the action of the second planetary gear mechanism, a certain transmission relationship exists among the rotor 171 of the first motor connected to the sun gear 153 of the second planetary gear mechanism, the first motor stator 172 and the second motor stator 182 connected to the ring gear 151 of the second planetary gear mechanism, and the carrier 152 of the second planetary gear mechanism.
When the automobile starts, one path of power transmitted to the planet carrier 142 of the first planetary gear and the planet carrier 152 of the second planetary gear is used as the output of the core transmission component and is increased continuously; one path of power transmitted to the sun gear 143 of the first planetary gear mechanism drives the transmission shaft 120 to rotate, and further, through the action of the third planetary gear mechanism, the sun gear 163 drives the rotor 181 of the second motor to rotate, at this time, the stator 182 of the second motor is driven by the ring gear 151 of the second planetary gear mechanism to rotate, the second motor is in a power generation state, under the control of the system, the generated electric energy can drive the first motor to operate, and the rotor 171 of the first motor drives the sun gear 153 of the second planetary gear mechanism to rotate, further, the rotation of the planet carrier 152 of the first motor is promoted under the action of the second planetary gear mechanism, and the torque increasing effect is achieved on the output of the core transmission component.
When the automobile needs to shift gears, the clutch 134 is disconnected, the operating mode of the first motor or the second motor is changed into a motor mode under the control of the system, the output rotating speed of the core transmission component is regulated and controlled under the action of the first motor or the second motor, the core transmission component directly reaches the rotating speed value required by the gear to be shifted, meanwhile, the gear relation of other gear sets of the automatic transmission is adjusted, and then the clutch 134 is combined to complete gear shifting. In the gear shifting process, the power of an engine does not need to be cut off, the gear shifting is soft, no impact is caused on a transmission system, the acceleration performance of the vehicle is good, and the vehicle does not have pause and frustration in running.
When the automobile runs on a long downhill or is braked, the system can control to increase the power generation torque of the first motor or the second motor so as to reduce the output rotating speed of the core component. In the deceleration braking, the energy can be recovered through the process before the braking, the output rotating speed is reduced, the vehicle speed is reduced when the brake pads are combined, and the braking performance is more reliable; when the vehicle runs on a long downhill, the energy can be recovered and the speed of the vehicle can be reduced in the process to realize the slow running of the vehicle, so that the service life of a brake element can be prolonged.
In specific implementation, the core transmission component further comprises a hollow shaft a131, a hollow shaft b132, a hollow shaft c133, a flange a191 and a motor base 193. The input shaft 110, the transmission shaft 120, the hollow shaft a131, the hollow shaft b132, the hollow shaft c133, the sun gear 143 of the first planetary gear mechanism, the sun gear 153 of the second planetary gear mechanism, and the sun gear 163 of the third planetary gear mechanism of the core transmission member are all concentrically arranged; one end of the input shaft 110 is fixedly connected with the ring gear 141 of the first planetary gear mechanism through a flange a191, the sun gear 143 of the first planetary gear mechanism is fixedly sleeved on the transmission shaft 120, one end of the transmission shaft 120 far away from the flange a191 is fixedly connected with the planet carrier 162 of the third planetary gear mechanism, and the motor base 193 is fixedly connected with the ring gear 161 of the third planetary gear mechanism; two ends of the hollow shaft a131 are respectively and fixedly connected with the planet carrier 142 of the first planetary gear mechanism and the planet carrier 152 of the second planetary gear mechanism, the clutch 134 is arranged in the hollow shaft a131, and the clutch 134 is used for realizing the connection and disconnection of the hollow shaft a131 and the transmission shaft 120; the hollow shaft b132 and the hollow shaft c133 are rotatably sleeved on the transmission shaft 120, the sun gear 153 of the second planetary gear mechanism and the rotor 171 of the first motor are fixedly sleeved on the hollow shaft b132, and the sun gear 163 of the third planetary gear mechanism and the rotor 181 of the second motor are fixedly sleeved on the hollow shaft c 133; motor cabinet 193 is hollow structure, and motor cabinet 193's one end and second planetary gear tooth ring 151 fixed connection, bayonet motor is all chooseed for use to first motor and second motor, and the equal fixed mounting of first motor and second motor is in motor cabinet 193. When the core transmission component is applied to a common vehicle, the third planetary gear mechanism and the hollow shaft c133 are omitted because the torque increasing function is not required, and the transmission shaft 120 is directly and fixedly connected with the rotor 181 of the second motor. The core transmission component is compact in overall structure, the hollow shaft a131 is sleeved with the gear to output power outwards, and the core transmission component can be applied to various different transmission structures to achieve uninterrupted power shifting and energy recovery of gearboxes with different speed ratios.
The following is a specific embodiment of the application of the core transmission component to an automatic transmission.
Example 1:
the overall structure of a non-cutting power shift automatic transmission is shown in fig. 3, and the core transmission component is shown in fig. 2, on the basis of the core transmission component, two intermediate shafts a210 and two intermediate shafts b220 are symmetrically arranged on two sides of an input shaft 110; an input driving gear 200 is fixedly sleeved on the input shaft 110, input driven gears 211 are fixedly sleeved on the two intermediate shafts a210, and the input driving gear 200 is meshed with the input driven gears 211; the hollow shaft a131 is fixedly sleeved with an output driving gear 130, two intermediate shafts b220 are fixedly sleeved with output driven gears 221, and the output driven gears 221 are meshed with the output driving gear 130; 7-15 driving gears 213, 5-13 driving gears 214, 3-11 driving gears 215 and 1-9 driving gears 216 are fixedly sleeved on the two intermediate shafts a210, 7-15 driven gears 233, 5-13 driven gears 234, 3-11 driven gears 235 and 1-9 driven gears 236 are further arranged in the transmission, the two 7-15 driving gears 213 are meshed with the 7-15 driven gears 233, the two 5-13 driving gears 214 are meshed with the 5-13 driven gears 234, the two 3-11 driving gears 215 are meshed with the 3-11 driven gears 235, and the two 1-9 driving gears 216 are meshed with the 1-9 driven gears 236; the two counter shafts b220 are fixedly sleeved with a 2-4-10-12 gear driving gear 222, a 6-8-14-16 gear driving gear 223 and a reverse gear driving gear 224, a 2-4-10-12 gear driven gear 238, a 6-8-14-16 gear driven gear 237, a reverse gear driven gear 232 and two reverse gear intermediate gears 212 are further arranged in the transmission, the two 2-4-10-12 gear driving gears 222 are meshed with the 2-4-10-12 gear driven gear 238, the two 6-8-14-16 gear driving gears 223 are meshed with the 6-8-14-16 gear driven gear 237, and the two reverse gear driving gears 224 are in transmission connection with the reverse gear driven gear 232 through the two reverse gear intermediate gears 212 respectively. A secondary shaft 230 is further arranged in the transmission, and a gear engaging sleeve a241, a gear engaging sleeve b242, a gear engaging sleeve c243, a 1-gear engaging sleeve 244 and a 9-gear engaging sleeve 245 are arranged on the secondary shaft 230; the gear coupling sleeve a241 serves to connect or disconnect the 2-4-10-12 driven gear 238 with or from the biaxial 230 and to connect or disconnect the 6-8-14-16 driven gear 237 with or from the biaxial 230, the gear coupling sleeve b242 serves to connect or disconnect the reverse driven gear 232 with or from the biaxial 230 and to connect or disconnect the 7-15 driven gear 233 with or from the biaxial 230, the gear coupling sleeve c243 serves to connect or disconnect the 5-13 driven gear 234 with or from the biaxial 230 and to connect or disconnect the 3-11 driven gear 235 with or from the biaxial 230, and the 1-1 coupling sleeve 244 serves to connect or disconnect the 1-9 driven gear 236 with or from the biaxial 230. The transmission also comprises a power output shaft 260, a secondary box planetary gear mechanism and a high-low gear combination sleeve 250, wherein the power output shaft 260 is fixedly connected with a planet carrier 252 of the secondary box planetary gear mechanism, a sun gear 251 of the secondary box planetary gear mechanism is fixedly sleeved on the secondary shaft 230, a 9-gear combination sleeve 245 is used for connecting or disconnecting a 1-9-gear driven gear 236 with the planet carrier 252 of the secondary box planetary gear mechanism, and the high-low gear combination sleeve 250 is used for connecting a ring gear 253 of the secondary box planetary gear mechanism with the planet carrier 252 of the secondary box planetary gear mechanism or connecting the ring gear 253 of the secondary box planetary gear mechanism with a transmission shell. The transmission further comprises a P-range gear 231, the P-range gear 231 being fixedly connected with a planet carrier 252 of the planetary gear mechanism.
The embodiment is a sixteen-speed automatic transmission, which is mainly applied to heavy-duty trucks and other large-sized vehicles, and has 7 gears during operation, namely a P gear, an N gear, an R gear, a D gear, a middle position in a manual mode, an addition position in the manual mode, and a subtraction position in the manual mode. In addition, three working modes of economy, power and mud are also arranged.
P gear: all gear combination sleeves are in the idle position, the P-gear 231 is locked, the planet carrier 252 of the auxiliary box planetary gear mechanism is simultaneously locked, the further power output shaft 260 is locked, and the automobile is in a parking state. In implementation, the P-gear 231 is locked by the P-gear hook, a P-gear electromagnetic air valve is additionally arranged on a pneumatic control loop of the automobile, and the P-gear hook is pushed by air pressure of the air-cut parking brake through a one-way valve to release the P-gear. When the parking air pressure is released, the P gear air pressure is not released due to the one-way valve, and the P gear is not combined until the transmission controller drives the P gear electromagnetic air valve to release the P gear air pressure after detecting that the power output shaft 260 has no rotating speed signal, and the P gear is combined.
N gear: all gear coupling sleeves are in the idle position, the secondary shaft 230 has no power input, and the power output shaft 260 is in a free state.
The R gear comprises four gears of R1, R2, R3 and R4, and the power transmission is as follows:
r1 gear: the high-low gear combination sleeve 250 is combined at a low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the transmission shell; a gear coupling sleeve b242 connects the reverse driven gear 232 with the secondary shaft 230; the clutch 134 disconnects the hollow shaft a131 from the drive shaft 120. At this time, the second motor is set to an electromagnetic braking state, and the power input from the input shaft 110 is reduced in speed by the first planetary gear mechanism, transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the reverse driving gear 224, the reverse intermediate gear 212, the reverse driven gear 232, the shift engaging sleeve b242, and the secondary shaft 230 in this order, reduced in speed by the sub-tank planetary gear mechanism, and output from the power output shaft 260.
R2 gear: the high-low gear combination sleeve 250 is combined at a low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the transmission shell; a gear coupling sleeve b242 connects the reverse driven gear 232 with the secondary shaft 230; the clutch 134 connects the hollow shaft a131 with the drive shaft 120. At this time, the power input from the input shaft 110 is directly transmitted through the carrier 142 of the first planetary gear mechanism, and then sequentially transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the reverse driving gear 224, the reverse intermediate gear 212, the reverse driven gear 232, the shift coupling sleeve b242, and the second shaft 230, and then reduced in speed by the sub-casing planetary gear mechanism, and then output from the power output shaft 260.
R3 gear: the high-low gear combination sleeve 250 is combined at a high-gear position, so that a gear ring 253 of the auxiliary box planetary gear mechanism is connected with a planet carrier 252 of the auxiliary box planetary gear mechanism; a gear coupling sleeve b242 connects the reverse driven gear 232 with the secondary shaft 230; the clutch 134 disconnects the hollow shaft a131 from the drive shaft 120. At this time, the second motor is set to an electromagnetic braking state, and the power input from the input shaft 110 is reduced in speed by the first planetary gear mechanism, transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the reverse driving gear 224, the reverse intermediate gear 212, the reverse driven gear 232, the shift coupling sleeve b242, and the secondary shaft 230 in this order, and directly output from the power output shaft 260.
R4 gear: the high-low gear combination sleeve 250 is combined at a high-gear position, so that a gear ring 253 of the auxiliary box planetary gear mechanism is connected with a planet carrier 252 of the auxiliary box planetary gear mechanism; a gear coupling sleeve b242 connects the reverse driven gear 232 with the secondary shaft 230; the clutch 134 connects the hollow shaft a131 with the drive shaft 120. At this time, the power input from the input shaft 110 is directly transmitted through the carrier 142 of the first planetary gear mechanism, and then sequentially transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the reverse driving gear 224, the reverse intermediate gear 212, the reverse driven gear 232, the shift coupling sleeve b242, and the second shaft 230, and then directly output from the power output shaft 260.
The D gear comprises sixteen gears, and the power transmission of each gear is as follows:
1, gear 1: the high-low gear combination sleeve 250 is combined at a low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the transmission shell; the 1 st engagement sleeve 244 connects the 1-9 th driven gear 236 with the secondary shaft 230. The power input from the input shaft 110 is transmitted sequentially through the input driving gear 200, the input driven gear 211, the intermediate shaft a210, the 1-9 driving gear 216, the 1-9 driven gear 236, the 1-gear engaging sleeve 244 and the secondary shaft 230, and then is reduced in speed by the auxiliary box planetary gear mechanism and then output by the power output shaft 260. At this time, the gear engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230, the clutch 134 disconnects the hollow shaft a131 from the transmission shaft 120, and the first motor and the second motor are in a free rotation state and do not output power, so as to conveniently intervene in electric power to realize gear shifting operation.
2, gear: the high-low gear combination sleeve 250 is combined at a low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the transmission shell; the range engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230; the clutch 134 disconnects the hollow shaft a131 from the drive shaft 120. At this time, the second motor is set to an electromagnetic braking state, and the power input from the input shaft 110 is reduced in speed by the first planetary gear mechanism, transmitted through the hollow shaft a131, the output drive gear 130, the output driven gear 221, the intermediate shaft b220, the 2-4-10-12 drive gear 222, the 2-4-10-12 driven gear 238, the range engaging sleeve a241, and the secondary shaft 230 in this order, reduced in speed by the auxiliary casing planetary gear mechanism, and output from the power output shaft 260.
3, gear 3: the high-low gear combination sleeve 250 is combined at a low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the transmission shell; the gear coupling sleeve c243 connects the 3-11 driven gear 235 with the secondary shaft 230. The power input from the input shaft 110 is transmitted through the input driving gear 200, the input driven gear 211, the intermediate shaft a210, the 3-11 driving gear 215, the 3-11 driven gear 235, the gear coupling sleeve c243, and the secondary shaft 230 in sequence, and then is reduced in speed by the auxiliary box planetary gear mechanism and then output by the power output shaft 260. At this time, the gear engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230, the clutch 134 disconnects the hollow shaft a131 from the transmission shaft 120, and both the first motor and the second motor are in a free rotation state, which does not perform power output and is used for conveniently intervening electric power to realize gear shifting operation.
4, gear 4: the high-low gear combination sleeve 250 is combined at a low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the transmission shell; the range engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230; the clutch 134 connects the hollow shaft a131 and the drive shaft 120. The power input from the input shaft 110 is directly output through the first planetary gear mechanism, transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the 2-4-10-12 driving gear 222, the 2-4-10-12 driven gear 238, the gear engaging sleeve a241 and the secondary shaft 230 in sequence, and then reduced by the auxiliary box planetary gear mechanism and output through the power output shaft 260.
5, gear: the high-low gear combination sleeve 250 is combined at a low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the transmission shell; the gear coupling sleeve c243 connects the 5-13 driven gear 234 with the secondary shaft 230. The power input from the input shaft 110 is transmitted through the input driving gear 200, the input driven gear 211, the intermediate shaft a210, the 5-13 driving gear 214, the 5-13 driven gear 234, the gear coupling sleeve c243, and the secondary shaft 230 in sequence, and then is reduced in speed by the auxiliary box planetary gear mechanism and then output from the power output shaft 260. At this time, the gear engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230 or connects the 6-8-14-16 driven gear 237 with the secondary shaft 230, the clutch 134 disconnects the hollow shaft a131 from the transmission shaft 120, and both the first motor and the second motor are in a free rotation state, which does not output power and is used for conveniently intervening electric power to realize gear shifting operation.
6, gear 6: the high-low gear combination sleeve 250 is combined at a low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the transmission shell; the range engaging sleeve a241 connects the 6-8-14-16 driven gear 237 with the secondary shaft 230; the clutch 134 disconnects the hollow shaft a131 from the drive shaft 120. At this time, the second motor is electromagnetically braked. The power input from the input shaft 110 is reduced in speed by the first planetary gear mechanism, then transmitted through the hollow shaft a131, the output drive gear 130, the output driven gear 221, the intermediate shaft b220, the 6-8-14-16 drive gear 223, the 6-8-14-16 driven gear 237, the shift engaging sleeve a241, and the secondary shaft 230 in this order, and then reduced in speed by the auxiliary box planetary gear mechanism and then output by the power output shaft 260.
7, gear: the high-low gear combination sleeve 250 is combined at a low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the transmission shell; the gear coupling sleeve b242 connects the 7-15 th driven gear 233 with the secondary shaft 230. The power input from the input shaft 110 is transmitted through the input driving gear 200, the input driven gear 211, the intermediate shaft a210, the 7-15 driving gear 213, the 7-15 driven gear 233, the shift coupling sleeve b242, and the secondary shaft 230 in sequence, and then is reduced in speed by the auxiliary box planetary gear mechanism and output from the power output shaft 260. At this time, the gear engaging sleeve a241 connects the 6-8-14-16 driven gear 237 with the secondary shaft 230, the clutch 134 disconnects the hollow shaft a131 from the transmission shaft 120, and both the first motor and the second motor are in a free rotation state, which does not perform power output and is used for conveniently intervening electric power to realize gear shifting operation.
And 8, gear: the high-low gear combination sleeve 250 is combined at a low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the transmission shell; the range engaging sleeve a241 connects the 6-8-14-16 driven gear 237 with the secondary shaft 230; the clutch 134 connects the hollow shaft a131 and the drive shaft 120. The power input from the input shaft 110 is directly output through the first planetary gear mechanism, transmitted through the hollow shaft a131, the output drive gear 130, the output driven gear 221, the intermediate shaft b220, the 6-8-14-16 stage drive gear 223, the 6-8-14-16 stage driven gear 237, the gear engaging sleeve a241, and the secondary shaft 230 in sequence, and then reduced in speed through the auxiliary box planetary gear mechanism and output through the power output shaft 260.
9, gear: the 9 th gear coupling 245 couples the 1 th to 9 th driven gears 236 to the carrier 252 of the sub-tank planetary gear mechanism, and the power input from the input shaft 110 is directly transmitted to the carrier 252 of the sub-tank planetary gear mechanism through the input driving gear 200, the input driven gear 211, the intermediate shaft a210, the 1 th to 9 th driving gear, and the 1 th to 9 th driven gear 236 in sequence, and is output by the power output shaft 260 under the action of the sub-tank planetary gear mechanism. The gear is a transition gear, and the high-low gear combination sleeve 250 is combined at the low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the shell of the transmission; or the high-low gear combination sleeve 250 is combined at the high gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is connected with the planet carrier 252 of the auxiliary box planetary gear mechanism. At this time, the gear coupling sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230; the clutch 134 keeps the hollow shaft a131 and the transmission shaft 120 in a disconnected state, and the first motor and the second motor are both in a free rotation state, which does not perform power output, and is used for conveniently intervening electric power to realize gear shifting operation.
10 gear: the high-low gear combination sleeve 250 is combined at a high-gear position, so that a gear ring 253 of the auxiliary box planetary gear mechanism is connected with a planet carrier 252 of the auxiliary box planetary gear mechanism; the range engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230; the clutch 134 disconnects the hollow shaft a131 from the drive shaft 120. The second motor is electromagnetically braked, and the power input from the input shaft 110 is split and reduced by the first planetary gear mechanism, then is transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the 2-4-10-12 driving gear 222, the 2-4-10-12 driven gear 238, the gear engaging sleeve a241 and the secondary shaft 230 in sequence, and then is directly output through the auxiliary box planetary gear mechanism and the output shaft 260.
11, gear: the high-low gear combination sleeve 250 is combined at a high-gear position, so that a gear ring 253 of the auxiliary box planetary gear mechanism is connected with a planet carrier 252 of the auxiliary box planetary gear mechanism; the gear coupling sleeve c243 couples the 3-11 driven gear 235 with the secondary shaft 230. The power input from the input shaft 110 is transmitted through the input driving gear 200, the input driven gear 211, the intermediate shaft a210, the 3-11 driving gear 215, the 3-11 driven gear 235, the gear coupling sleeve c243, and the secondary shaft 230 in sequence, and then directly output through the auxiliary box planetary gear and the output shaft 260. In this gear, the gear engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230; the clutch 134 keeps the hollow shaft a131 and the transmission shaft 120 in a disconnected state, and the first motor and the second motor are both in a free rotation state, which does not perform power output, and is used for conveniently intervening electric power to realize gear shifting operation.
12, gear: the high-low gear combination sleeve 250 is combined at a high-gear position, so that a gear ring 253 of the auxiliary box planetary gear mechanism is connected with a planet carrier 252 of the auxiliary box planetary gear mechanism; the range engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230; the clutch 134 connects the hollow shaft a131 and the drive shaft 120. The power input from the input shaft 110 is directly output through the first planetary gear mechanism, and is directly output through the sub-tank planetary gear mechanism and the output shaft 260 after being sequentially transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the 2-4-10-12 driving gear 222, the 2-4-10-12 driven gear 238, the shift engaging sleeve a241, and the secondary shaft 230.
13 gear: the high-low gear combination sleeve 250 is combined at a high-gear position, so that a gear ring 253 of the auxiliary box planetary gear mechanism is connected with a planet carrier 252 of the auxiliary box planetary gear mechanism; the gear coupling sleeve c243 connects the 5-13 driven gear 234 with the secondary shaft 230. The power input from the input shaft 110 is transmitted through the input driving gear 200, the input driven gear 211, the intermediate shaft a210, the 5-13 driving gear 214, the 5-13 driven gear 234, the gear coupling sleeve c243, and the secondary shaft 230 in sequence, and then directly output through the auxiliary box planetary gear and the output shaft 260. At this time, the gear engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230 or connects the 6-8-14-16 driven gear 237 with the secondary shaft 230, the clutch 134 disconnects the hollow shaft a131 from the transmission shaft 120, and both the first motor and the second motor are in a free rotation state, which does not output power and is used for conveniently intervening electric power to realize gear shifting operation.
14 gear: the high-low gear combination sleeve 250 is combined at a high-gear position, so that a gear ring 253 of the auxiliary box planetary gear mechanism is connected with a planet carrier 252 of the auxiliary box planetary gear mechanism; the range engaging sleeve a241 connects the 6-8-14-16 driven gear 237 with the secondary shaft 230; the clutch 134 disconnects the hollow shaft a131 from the drive shaft 120. At this time, the second motor is electromagnetically braked. The power input from the input shaft 110 is reduced in speed by the first planetary gear mechanism, and then is transmitted through the hollow shaft a131, the output drive gear 130, the output driven gear 221, the intermediate shaft b220, the 6-8-14-16 drive gear 223, the 6-8-14-16 driven gear 237, the shift engaging sleeve a241, and the secondary shaft 230 in this order, and then is directly output through the auxiliary casing planetary gear mechanism and the output shaft 260.
15, gear: the high-low gear combination sleeve 250 is combined at a high-gear position, so that a gear ring 253 of the auxiliary box planetary gear mechanism is connected with a planet carrier 252 of the auxiliary box planetary gear mechanism; the gear coupling sleeve b242 connects the 7-15 th driven gear 233 with the secondary shaft 230. The power input from the input shaft 110 is transmitted through the input driving gear 200, the input driven gear 211, the intermediate shaft a210, the 7-15 driving gear 213, the 7-15 driven gear 233, the shift coupling sleeve b242, and the secondary shaft 230 in sequence, and then directly output through the auxiliary planetary gear set and the output shaft 260. At this time, the gear engaging sleeve a241 connects the 6-8-14-16 driven gear 237 with the secondary shaft 230, the clutch 134 disconnects the hollow shaft a131 from the transmission shaft 120, and both the first motor and the second motor are in a free rotation state, which does not perform power output and is used for conveniently intervening electric power to realize gear shifting operation.
16 gear: the high-low gear combination sleeve 250 is combined at a high-gear position, so that a gear ring 253 of the auxiliary box planetary gear mechanism is connected with a planet carrier 252 of the auxiliary box planetary gear mechanism; the range engaging sleeve a241 connects the 6-8-14-16 driven gear 237 with the secondary shaft 230; the clutch 134 connects the hollow shaft a131 and the drive shaft 120. The power input from the input shaft 110 is directly output through the first planetary gear mechanism, and is directly output through the sub-tank planetary gear mechanism and the output shaft 260 after being sequentially transmitted through the hollow shaft a131, the output drive gear 130, the output driven gear 221, the intermediate shaft b220, the 6-8-14-16 stage drive gear 223, the 6-8-14-16 stage driven gear 237, the gear engaging sleeve a241, and the secondary shaft 230.
When the vehicle starts, the high-low gear combination sleeve 250 is combined at a low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the shell of the transmission; the range sleeve a241 is coupled to connect the 2-4-10-12 driven gear 238 with the secondary shaft 230. The torque of the engine is transmitted to the ring gear 141 of the first planetary gear mechanism via the input shaft 110, and the torque is transmitted in two paths. One of the torques is transmitted to the hollow shaft a131 via the carrier 142 of the first planetary gear mechanism. The other path of torque is transmitted to the second motor through the sun gear 143 and the transmission shaft 120 of the first planetary gear mechanism to generate power, the generated electric energy acts on the first motor to enable the first motor to enter a motor working mode and be converted into kinetic energy, the kinetic energy is fed back to the hollow shaft a131 through the planet carrier 152 of the second planetary gear mechanism, and the torque increasing effect is achieved on the hollow shaft a 131. The resultant torque on the hollow shaft a131 is transmitted to the intermediate shaft b220 through the output driving gear 130 and the output driven gear 221, and then transmitted through the 2-4-10-12 gear driving gear 222, the 2-4-10-12 gear driven gear 238, the gear engaging sleeve a241 and the secondary shaft 230, and then is output through the power output shaft 260 after being decelerated through the auxiliary box planetary gear mechanism, so that the vehicle starts. The specific gear after the vehicle starts can be selected from any gear from 1 to 5, and is determined by monitoring parameters such as a load signal of an engine, an accelerator pedal position, a first motor running current and a second motor running current and combining with the vehicle acceleration calculated by a transmission output rotating speed signal. When the specific gear after starting is determined, if the gear is higher than 2 gears, the control system of the vehicle controls the second motor to be switched to the motor working mode, and the first motor is switched to the motor working mode.
When the vehicle starts in a reverse gear, the high-low gear combination sleeve 250 is combined at a low gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is fixedly connected with the shell of the transmission; the range engaging sleeve a241 is in the neutral position, disconnecting the 2-4-10-12 driven gear 238 from the secondary shaft 230 and disconnecting the 6-8-14-16 driven gear 237 from the secondary shaft 230; the gear coupling sleeve b242 couples the reverse driven gear 232 to the secondary shaft 230. The starting process is the same as the vehicle forward starting process, the torque synthesized on the hollow shaft a131 is transmitted to the intermediate shaft b220 through the output driving gear 130 and the output driven gear 221, then transmitted through the reverse driving gear 224, the reverse intermediate gear 212, the reverse driven gear 232, the gear combination sleeve b242 and the secondary shaft 230, and is output by the power output shaft 260 after being decelerated by the auxiliary box planetary gear mechanism, and the vehicle is started.
When the vehicle is shifted up from 1 gear to 2 gear, the generated torque of the second motor and the driving power of the first motor in the motor mode are increased under the control of the control system of the vehicle, and the generated torque can be transmitted to the second shaft 230 through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the 2-4-10-12 driving gear 222, the 2-4-10-12 driven gear 238 and the gear engaging sleeve a 241. In this process, the torque generated by the first electric machine acting as a motor causes the operating state of the secondary shaft 230 to be the same as that when the vehicle is running in gear 1, and the gear 1 sleeve 244 no longer transmits torque and can be directly disconnected under the control of the control system. And then, continuously increasing the generating torque of the second motor until the second motor stops rotating, applying current brake to the second motor, completing the gear shifting process and outputting the 2 nd gear.
When the vehicle is shifted from 2 to 3, under the control of a control system of the vehicle, the first motor is in a motor mode, the second motor is changed into a motor driving mode, the driving speed of the second motor is gradually increased, the second motor is transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the 2-4-10-12 driving gear 222, the 2-4-10-12 driven gear 238 and the gear engaging sleeve a241, the speed on the secondary shaft 230 is gradually increased, when the output speed of the second motor is synchronous with the required speed of 3, the gear engaging sleeve c243 is combined to connect the 3-11 driven gear 235 with the secondary shaft 230, and simultaneously the second motor is out of a driving state and rotates freely to complete the gear shifting process and output of 3.
When the vehicle is shifted from 3 to 4, under the control of a control system of the vehicle, the second motor is used as a driving motor, the driving torque of the second motor is increased, the gear coupling sleeve c243 is disconnected when the torque is not transmitted by the gear coupling sleeve c243, then the rotating speed of the second motor is gradually increased, the second motor is transmitted by the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the 2-4-10-12 driving gear 222, the 2-4-10-12 driven gear 238 and the gear coupling sleeve a241, the rotating speed on the second shaft 230 is gradually increased, and when the output rotating speed of the second motor is synchronous with the required rotating speed of 4, the clutch 134 is controlled to be combined to enable the hollow shaft a131 and the transmission shaft 120 to be in a connected state, the gear shifting process is completed, and 4-gear output is realized.
When the vehicle is shifted from 4-gear to 5-gear, under the control of a control system of the vehicle, the second motor is used as a driving motor, the driving torque is increased, the clutch 134 is disconnected when the clutch 134 does not transmit torque, then the rotation speed of the second motor is gradually increased, the second motor is transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the 2-4-10-12 driving gear 222, the 2-4-10-12 driven gear 238 and the gear engaging sleeve a241, the rotation speed on the second shaft 230 is gradually increased, and when the output rotation speed of the second motor is synchronous with the rotation speed required by 5-gear, the gear engaging sleeve c243 is combined to connect the 5-13 driven gear 234 with the second shaft 230, so that the gear shifting process is completed, and 5-gear output is realized.
In the upshifting process of the 1 gear to the 5 gears, the basic working process is the same, so that in practical use, the gear shifting can be completed only by increasing the driving rotating speed of the second motor to enable the output rotating speed to reach the gear to be shifted and enable the gear engaging sleeve or the clutch corresponding to the gear to be combined. Therefore, the automatic transmission can support the step-over type upshifting of any gear in the range of 1-5 gears.
When the vehicle is shifted up from 5 to 6, the gear engaging sleeve a241 is combined to connect the 6-8-14-16 driven gear 237 with the two shafts 230, the power generation torque of the second motor and the driving power of the first motor are increased under the control of the control system of the vehicle until the gear engaging sleeve c243 does not transmit torque, the gear engaging sleeve c243 is disconnected, the power generation torque of the second motor is continuously increased until the gear engaging sleeve c243 stops rotating, the current brake is applied again, the gear shifting process is completed, and 6-gear output is realized.
When the vehicle is shifted from 6 to 7, under the control of a control system of the vehicle, the first motor is changed into a motor state, the second motor is changed into a driving motor, the rotating speed of the second motor is gradually increased, when the output rotating speed is synchronous with the rotating speed required by 7, the gear combination sleeve b242 is combined to enable the 7-15 gear driven gear 233 to be connected with the secondary shaft 230, the second motor is driven to quit, the second motor rotates freely, the gear shifting process is completed, and 7-gear output is achieved.
When the vehicle is shifted from 7 to 8, under the control of a control system of the vehicle, the driving torque of the second motor is increased until the gear combination sleeve b242 does not transmit torque, the gear combination sleeve b242 is disconnected, the rotating speed of the second motor is gradually increased, and when the output rotating speed is synchronous with the rotating speed required by 8, the clutch 134 is controlled to be combined to enable the hollow shaft a131 and the transmission shaft 120 to be in a connected state, so that the gear shifting process is completed, and 8-gear output is realized.
When the vehicle is shifted from 8 th gear to 9 th gear, under the control of a control system of the vehicle, the driving torque of the second motor is increased until the clutch 134 is disconnected when the clutch 134 does not transmit torque, then the rotating speed of the second motor is gradually increased, and when the output rotating speed is synchronous with the rotating speed required by 9 th gear, the 9 th gear combination sleeve 245 is combined to connect the 1-9 th gear driven gear 236 with the planet carrier 252 of the auxiliary box planetary gear mechanism, so that the gear shifting process is completed, and 9 th gear is output.
Similarly, the basic working process of the upshifting process from 5 gears to 9 gears is the same, and the automatic transmission can support the step-over type upshifting of any gear in the 5-9 gear range in practical use.
The operation flow of the vehicle for the 10 th gear shift from the 9 th gear is the same as the operation flow of the 2 nd gear shift from the 1 st gear, the operation flow of the 11 th gear shift from the 10 th gear is the same as the operation flow of the 3 rd gear shift from the 2 nd gear, the operation flow of the 12 th gear shift from the 11 th gear shift is the same as the operation flow of the 4 th gear shift from the 3 rd gear shift, the operation flow of the 12 th gear shift 13 is the same as the operation flow of the 5 th gear shift from the 4 th gear shift, the operation flow of the 13 th gear shift 14 is the same as the operation flow of the 6 th gear shift from the 5 th gear shift 6, the operation flow of the 14 th gear shift 15 th gear shift is the same as the operation flow of the 7 th gear shift from the 7 th gear shift, the operation flow of the 15 th gear shift 16 th gear shift is the same as the operation flow of the 7 th gear shift 8 th gear shift, and the power transmission is only distinguished in that the high-low gear shift combination sleeve 250 is changed from the low gear position to the high gear position combination, and the ring gear 253 of the auxiliary box planetary gear mechanism is connected with the carrier 252 of the auxiliary box planetary gear mechanism, and the above-mentioned-up flow will not be repeated. Similarly, the automatic transmission can realize the step-over type upshifting in two shifting intervals of 9-13 gears and 13-16 gears.
When the vehicle is shifted from 16 to 15, under the control of the control system of the vehicle, the driving torque of the second motor as a motor is increased first until the clutch 134 is disconnected when the clutch 134 does not transmit torque, then the driving torque of the second motor is gradually reduced to reduce the rotation speed, and when the output rotation speed is reduced to be the same as the 15-gear running rotation speed, the gear combination sleeve b242 is combined to connect the 7-15-gear driven gear 233 with the secondary shaft 230 to complete the gear shifting and output from 15.
When the vehicle is shifted from 15 th gear to 14 th gear, under the control of the control system of the vehicle, the driving torque of the second motor as a motor is increased until the gear coupling sleeve b242 is disconnected when no torque is transmitted, then the driving torque of the second motor is gradually reduced to reduce the rotating speed, and when the output rotating speed is reduced to be the same as the 14 th operating rotating speed, the gear coupling sleeve a241 connects the 6-8-14-16 th driven gear 237 with the secondary shaft 230 to complete the gear shifting and output from 14 th gear.
When the vehicle is reduced from 14-gear to 13-gear, under the control of a control system of the vehicle, the braking current of the second motor is released, the second motor works in a motor mode, part of energy is recovered in the process of downshifting, the output rotating speed of the transmission is gradually reduced under the power generation load until the speed ratio is reduced to 13-gear, the gear combination sleeve c243 is combined to connect the 5-13-gear driven gear 234 with the secondary shaft 230, the second motor is in a free rotation state, the gear shifting is completed, and the 13-gear output is realized.
When the vehicle is shifted down from 13 to 12, the gear engaging sleeve a241 is combined to connect the 2-4-10-12 driven gear 238 with the secondary shaft 230, under the control of the control system of the vehicle, the power generation torque of the second motor and the driving torque of the first motor as a motor are increased firstly until the gear engaging sleeve c243 does not transmit torque, the combined state is exited, then the rotation speed of the second motor is reduced step by step, when the output rotation speed reaches the rotation speed matched with the 12-gear speed ratio, the clutch 134 is combined to enable the hollow shaft a131 and the transmission shaft 120 to be in the connected state, the gear shifting is completed, and the 12-gear output is realized.
When the vehicle is shifted from 12 to 11, under the control of the control system of the vehicle, the driving torque of the second motor as a motor is increased firstly until the clutch 134 is out of the combination state when the torque is not transmitted, then the rotating speed of the second motor is gradually reduced, and when the output rotating speed is synchronous with the rotating speed required by 11, the gear combination sleeve c243 is combined to connect the 3-11 driven gear 235 with the second shaft 230, so that the gear shifting process is completed and the output is carried out by 11.
When the vehicle is shifted down from 11-gear to 10-gear, under the control of a control system of the vehicle, the driving torque of the second motor serving as a motor is increased firstly until the gear combination sleeve c243 is not transmitted with torque, the combination state is exited, then the rotating speed of the second motor is gradually reduced, when the second motor stops rotating, current is applied to the second motor to perform electromagnetic braking, the gear shifting process is completed, and the second motor is output from 10-gear.
When the vehicle is shifted down from 10 to 9, under the control of a control system of the vehicle, the braking current of the second motor is released, the second motor works in a motor mode, part of energy is recovered in the process of shifting down, the output rotating speed of the transmission is gradually reduced under the power generation load until the speed is reduced to reach 9, the 9-gear combination sleeve 245 is combined to connect the 1-9-gear driven gear 236 with the planet carrier 252 of the auxiliary box planetary gear mechanism, the shifting process is completed, and 9-gear output is realized.
When the vehicle shifts from 9 to 8, the high-low gear combination sleeve 250 is combined at a high-gear position, so that the gear ring 253 of the auxiliary box planetary gear mechanism is connected with the planet carrier 252 of the auxiliary box planetary gear mechanism; the range sleeve a241 is coupled to connect the 6-8-14-16 driven gear 237 with the secondary shaft 230. Under the control of the control system of the vehicle, the driving torque of the second motor as a motor is firstly increased until the 9-gear coupling sleeve 245 is not used for transmitting the torque, the coupling state is disconnected, then the rotating speed of the second motor is gradually reduced, when the output rotating speed reaches the rotating speed corresponding to the 8-gear speed ratio,
the 9-gear and 8-gear reduction process: the auxiliary box combining sleeve is combined with a high-gear position, the gear combining sleeve (15) is combined with 6, 8, 14 and 16 gear positions, the driving torque of the motor 2(11) is increased, the 9-gear combining sleeve (32) does not transmit torque, the 9-gear combining sleeve (32) is separated from combination, the rotating speed of the motor 2(11) is gradually reduced, and when the 8-gear speed ratio is reached, the clutch 134 is combined to enable the hollow shaft a131 and the transmission shaft 120 to be in a connection state, gear shifting is completed, and 8-gear output is achieved.
The operation flow of the vehicle for descending from 8 th gear to 7 th gear is the same as the operation flow of descending from 16 th gear to 15 th gear, the operation flow of the vehicle for descending from 7 th gear to 6 th gear is the same as the operation flow of descending from 15 th gear to 14 th gear, the operation flow of the vehicle for descending from 6 th gear to 5 th gear is the same as the operation flow of descending from 14 th gear to 13 th gear, the operation flow of the vehicle for descending from 5 th gear to 4 th gear is the same as the operation flow of descending from 4 th gear to 3 th gear to 12 th gear to 11 th gear, the operation flow of the vehicle for descending from 3 rd gear to 2 th gear is the same as the operation flow of descending from 11 th gear to 10 th gear, and the operation flow of the vehicle for descending from 2 nd gear to 1 st gear is the same as the operation flow of descending from 10 th gear to 9 th gear, and will not be described herein again. Likewise, the transmission may support a skip-through downshift in the 1-5, 5-9, 9-13, and 13-16 ranges.
The economy mode and the power mode of the transmission are used on a common road, and in the economy mode, the gear shifting rotating speed is low, and the work of the transmission is biased to save energy; in power mode, the shift speed is high and the transmission operation is biased toward vehicle acceleration performance. When the transmission is in a muddy mode, each gear combination sleeve is forbidden to be combined with odd gears, the clutch 134 is forbidden to be combined, the transmission works in a hybrid power driving mode, the first motor or the second motor is used for entering a motor mode, kinetic energy is provided in an auxiliary mode, and the acceleration performance of the vehicle is fully improved.
The retarding function of the transmission can be realized in a manual mode and a braking mode.
Under the manual mode, turn on the retarber switch, adjust the retarding power to corresponding gear, first motor and second motor all are in the electricity generation mode, and the electric energy that its produced preferentially satisfies the battery and charges, and unnecessary electric energy distributes through electric heater conversion heat energy. When the power generated by the motor is larger, the engine exhaust brake can be started to jointly brake and slow.
Under the braking mode, the generated power of the motor is controlled by detecting the pressure of the control air passages 1 and 2 output by the brake master cylinder, the other two groups of air passage control pressure are output, and the back pressure of the brake relay valve driving piston is controlled, so that the pressure of the brake shoe is reduced. When the braking torque is large, the engine exhaust brake is started to perform braking together.
Example 2:
as shown in fig. 4, in addition to the above-described sixteen-speed automatic transmission structure, the power output shaft 260, the auxiliary planetary gear mechanism, the high-low gear coupling sleeve 250, and the 9-speed coupling sleeve 245 are eliminated, and the P-speed gear 231 is directly connected to the secondary shaft 230 and directly outputs the power through the secondary shaft 230, so that the transmission can be converted into an eight-speed transmission, which is mainly applied to automatic transmission of vehicles such as large passenger cars.
The main gears are arranged as follows:
p gear: all gear combination sleeves are in the empty position, the P-gear 231 is directly locked, and the automobile is in a parking state.
N gear: all gear combination sleeves are in the empty position, the secondary shaft 230 is in the free position, and no power is output.
The R gear comprises two gears R1 and R2, and the power transmission is as follows:
r1 gear: a gear coupling sleeve b242 connects the reverse driven gear 232 with the secondary shaft 230; the clutch 134 disconnects the hollow shaft a131 from the drive shaft 120. At this time, the second motor is set to an electromagnetic braking state, and the power input from the input shaft 110 is reduced in speed by the first planetary gear mechanism, transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the reverse driving gear 224, the reverse intermediate gear 212, the reverse driven gear 232, and the shift coupling sleeve b242 in this order, and directly output from the second shaft 230.
R2 gear: a gear coupling sleeve b242 connects the reverse driven gear 232 with the secondary shaft 230; the clutch 134 connects the hollow shaft a131 with the drive shaft 120. At this time, the power input from the input shaft 110 is directly transmitted through the carrier 142 of the first planetary gear mechanism, and then is directly output from the second shaft 230 after being sequentially transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the reverse driving gear 224, the reverse intermediate gear 212, the reverse driven gear 232, and the shift coupling sleeve b 242.
The D gear comprises eight gears, and the power transmission of each gear is as follows:
1, gear 1: the 1 st engagement sleeve 244 connects the 1-9 th driven gear 236 with the secondary shaft 230. The power input from the input shaft 110 is transmitted through the input driving gear 200, the input driven gear 211, the intermediate shaft a210, the 1-9 driving gear 216, the 1-9 driven gear 236, and the 1-gear engaging sleeve 244 in sequence, and then output from the secondary shaft 230. At this time, the gear engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230, the clutch 134 disconnects the hollow shaft a131 from the transmission shaft 120, and the first motor and the second motor are in a free rotation state and do not output power, so as to conveniently intervene in electric power to realize gear shifting operation.
2, gear: the range engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230; the clutch 134 disconnects the hollow shaft a131 from the drive shaft 120. At this time, the second motor is set to an electromagnetic braking state, and the power input from the input shaft 110 is reduced by the first planetary gear mechanism, and then transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the 2-4-10-12 driving gear 222, the 2-4-10-12 driven gear 238, and the range engaging sleeve a241 in this order, and then output from the second shaft 230.
3, gear 3: the gear coupling sleeve c243 connects the 3-11 driven gear 235 with the secondary shaft 230. The power input from the input shaft 110 is transmitted through the input driving gear 200, the input driven gear 211, the intermediate shaft a210, the 3-11 driving gear 215, the 3-11 driven gear 235, and the gear coupling sleeve c243 in sequence, and then output from the secondary shaft 230. At this time, the gear engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230, the clutch 134 disconnects the hollow shaft a131 from the transmission shaft 120, and both the first motor and the second motor are in a free rotation state, which does not perform power output and is used for conveniently intervening electric power to realize gear shifting operation.
4, gear 4: the range engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230; the clutch 134 connects the hollow shaft a131 and the drive shaft 120. The power input from the input shaft 110 is directly output through the first planetary gear mechanism, and is transmitted through the hollow shaft a131, the output driving gear 130, the output driven gear 221, the intermediate shaft b220, the 2-4-10-12 driving gear 222, the 2-4-10-12 driven gear 238, and the shift engaging sleeve a241 in this order, and then output from the second shaft 230.
5, gear: the gear coupling sleeve c243 connects the 5-13 driven gear 234 with the secondary shaft 230. The power input from the input shaft 110 is transmitted through the input driving gear 200, the input driven gear 211, the intermediate shaft a210, the 5-13 driving gear 214, the 5-13 driven gear 234, and the range coupling sleeve c243 in sequence, and then output from the secondary shaft 230. At this time, the gear engaging sleeve a241 connects the 2-4-10-12 driven gear 238 with the secondary shaft 230 or connects the 6-8-14-16 driven gear 237 with the secondary shaft 230, the clutch 134 disconnects the hollow shaft a131 from the transmission shaft 120, and both the first motor and the second motor are in a free rotation state, which does not output power and is used for conveniently intervening electric power to realize gear shifting operation.
6, gear 6: the range engaging sleeve a241 connects the 6-8-14-16 driven gear 237 with the secondary shaft 230; the clutch 134 disconnects the hollow shaft a131 from the drive shaft 120. At this time, the second motor is electromagnetically braked. The power input from the input shaft 110 is reduced in speed by the first planetary gear mechanism, and then transmitted through the hollow shaft a131, the output drive gear 130, the output driven gear 221, the intermediate shaft b220, the 6-8-14-16 drive gear 223, the 6-8-14-16 driven gear 237, and the range engagement sleeve a241 in this order, and then output from the second shaft 230.
7, gear: the gear coupling sleeve b242 connects the 7-15 th driven gear 233 with the secondary shaft 230. The power input from the input shaft 110 is transmitted through the input driving gear 200, the input driven gear 211, the intermediate shaft a210, the 7-15 driving gear 213, the 7-15 driven gear 233, and the shift coupling sleeve b242 in sequence, and then output from the secondary shaft 230. At this time, the gear engaging sleeve a241 connects the 6-8-14-16 driven gear 237 with the secondary shaft 230, the clutch 134 disconnects the hollow shaft a131 from the transmission shaft 120, and both the first motor and the second motor are in a free rotation state, which does not perform power output and is used for conveniently intervening electric power to realize gear shifting operation.
And 8, gear: the range engaging sleeve a241 connects the 6-8-14-16 driven gear 237 with the secondary shaft 230; the clutch 134 connects the hollow shaft a131 and the drive shaft 120. The power input from the input shaft 110 is directly output through the first planetary gear mechanism, and is transmitted through the hollow shaft a131, the output drive gear 130, the output driven gear 221, the intermediate shaft b220, the 6-8-14-16 drive gear 223, the 6-8-14-16 driven gear 237, and the shift engagement sleeve a241 in this order, and then output from the second shaft 230.
As can be seen from the above, in this embodiment 2, on the basis of the above embodiment 1, structures such as the auxiliary box planetary gear mechanism are omitted, only the eight-speed transmission function is retained, and the upshift and downshift process of the embodiment 2 is substantially the same as the gear upshift and downshift process of the first eight gears in embodiment 1, and details are not repeated here. The eight-speed transmission can still realize power-off-free gear shifting and energy recovery, and is very suitable for the use requirements of vehicles such as large buses and the like.
Example 3:
the overall structure of a non-power-off automatic transmission is shown in fig. 5, and the core transmission components are shown in fig. 1. The uninterrupted power shifting automatic transmission structure further comprises a shell on the basis of the core transmission component, wherein a transmission shaft a310, a hollow shaft d320, a hollow shaft e330, a Ravigneaux planetary gear mechanism and a single-row double-stage planetary gear mechanism are arranged in the shell. The double planetary gear mechanism is commonly found in a ravigneaux planetary gear automatic transmission and comprises a gear ring, outer planetary gears, inner planetary gears, a planet carrier and a sun gear, wherein the gear ring and the sun gear are concentrically arranged, the sun gear is externally meshed with a plurality of inner planetary gears, the gear ring is internally meshed with a plurality of outer planetary gears, the outer planetary gears are meshed with the inner planetary gears, and the planet carrier is used for keeping and supporting the inner planetary gears and the outer planetary gears. The transmission shaft a310, the hollow shaft d320 and the hollow shaft e330 are concentrically arranged, the transmission shaft a310 penetrates through the hollow shaft d320, and two ends of the transmission shaft a respectively extend out of two ends of the hollow shaft e 330; the hollow shaft d320 is inserted into the hollow shaft e330, and two ends of the hollow shaft d320 respectively extend out of two ends of the hollow shaft e 330. One end of the transmission shaft a310 is fixedly sleeved with a driven main gear 311, the input shaft 110 is fixedly sleeved with a driving main gear 300, and the driven main gear 311 is meshed with the driving main gear 300. The other end of the transmission shaft a310 is fixedly connected with a sun gear 312 of the single-row double-stage planetary gear mechanism, and a planet carrier 313 of the single-row double-stage planetary gear mechanism is fixedly connected with the shell. The hollow shaft d320 is fixedly connected with a sun gear 322 of the Ravigneaux planetary gear mechanism, an outer gear 326 is sleeved outside a gear ring 325 of the Ravigneaux planetary gear mechanism, an output driving gear 130 is fixedly sleeved on the hollow shaft a131 of the core transmission part, the outer gear 326 is meshed with the output driving gear 130, and the outer gear 326 is used for outputting and is in transmission connection with a differential 390 of a vehicle. A transmission gear a331 is fixedly arranged on the hollow shaft e330, a transmission gear b332 is coaxially and fixedly connected to the outer planetary gear 324 of the ravigneaux planetary gear mechanism, and the transmission gear a331 is meshed with the transmission gear b 332.
The automatic transmission further includes a clutched shifting device a340, a clutched shifting device b350, a clutched shifting device c360, a clutched shifting device d370, and a clutched shifting device e 380. The clutch shifting device a340 is used for connecting or disconnecting the ring gear 315 of the single-row double-stage planetary gear mechanism with or from the hollow shaft d320, the clutch shifting device b350 is used for connecting or disconnecting the ring gear 315 of the single-row double-stage planetary gear mechanism with or from the hollow shaft e330, the clutch shifting device c360 is used for connecting or disconnecting the hollow shaft e330 with or from the housing, the clutch shifting device d370 is used for connecting or disconnecting the planet carrier 323 of the Ravigneaux planetary gear mechanism with or from the housing, and the clutch shifting device e380 is used for connecting or disconnecting the planet carrier 323 of the Ravigneaux planetary gear mechanism with or from the transmission shaft a 310.
The automatic transmission in the embodiment can realize eight-speed automatic speed regulation, can realize non-cut-off power gear shifting and energy recovery by relying on the core transmission part, and is very suitable for the use requirements of vehicles such as cars and the like as a transverse automatic transmission. The main gears are arranged as follows:
p gear: all the clutch shifting devices and the clutch 134 are in an off state, the transmission shaft a310 is locked by a P-range gear (not shown), and the vehicle is in a parking state.
N gear: all clutching and shifting devices and the clutch 134 are in an open state, and the external gear 326 for output is in a free state, with no power output.
R gear: direct reverse gear output and electric reverse gear output are divided. In a conventional mode, the reverse gear is only a short distance, and the reverse gear is generally driven by a motor in a reverse direction to perform electric reverse gear. When the direct reverse gear is output, the clutch shifting device b350 and the clutch shifting device d370 are connected, and the other clutch shifting devices and the clutch 134 are disconnected, at this time, the power input by the input shaft 110 is transmitted through the driving main gear 300, the driven main gear 311, the transmission shaft a310, the sun gear 312 of the single-row two-stage planetary gear mechanism, the ring gear 315 of the single-row two-stage planetary gear mechanism, the clutch shifting device b350, the hollow shaft e330, the outer planetary gear 324 of the ravigneaux planetary gear mechanism, and the ring gear 325 of the ravigneaux planetary gear mechanism in sequence, and then is output to the differential 390 of the vehicle through the outer gear 326.
The D gear comprises eight gears, and the power transmission of each gear is as follows:
1, gear 1: the clutch shifting device a340 and the clutch shifting device d370 are connected, and the other clutch shifting devices and the clutch 134 are disconnected, so that the power input from the input shaft 110 is transmitted through the driving main gear 300, the driven main gear 311, the transmission shaft a310, the sun gear 312 of the single-row double-stage planetary gear mechanism, the ring gear 315 of the single-row double-stage planetary gear mechanism, the clutch shifting device a340, the hollow shaft d320, and the sun gear 322 of the ravigneaux planetary gear mechanism in sequence, and at this time, because the clutch shifting device d370 is connected, the carrier 323 of the ravigneaux planetary gear mechanism is fixed, and the transmitted power is freely transmitted to the ring gear 325 of the ravigneaux planetary gear mechanism and is output to the external differential gear 390 of the vehicle by the clutch shifting device d 326. When the vehicle runs in the gear, the second electric machine runs reversely relative to the rotation direction of the input shaft 110, and works in a power generation mode, and the generated electric energy is stored in the battery to realize partial energy recovery.
2, gear: the clutch shifting device a340 and the clutch shifting device c360 are in a connected state, other clutch shifting devices and the clutch 134 are in a disconnected state, at this time, power input by the input shaft 110 is transmitted through the driving main gear 300, the driven main gear 311, the transmission shaft a310, the sun gear 312 of the single-row double-stage planetary gear mechanism, the ring gear 315 of the single-row double-stage planetary gear mechanism, the clutch shifting device a340, the hollow shaft d320 and the sun gear 322 of the ravigneaux planetary gear mechanism in sequence, at this time, because the clutch shifting device c360 is in a connected state, the hollow shaft e330 is fixed, and further restraint is caused on the outer planet gear 324 of the ravigneaux planetary gear mechanism, the transmission mode of the ravigneaux planetary gear mechanism is changed relative to the 1 st gear state, and finally, power is transmitted through the ring gear 325 in a new mode and is output to the differential 390 of the vehicle by the outer gear 326. When the vehicle runs in the gear, the second electric machine runs reversely relative to the rotation direction of the input shaft 110, and works in a power generation mode, and the generated electric energy is stored in the battery to realize partial energy recovery.
3, gear 3: the clutch shifting device a340 and the clutch shifting device b350 are in a connected state, other clutch shifting devices and the clutch 134 are in a disconnected state, at the moment, power input by the input shaft 110 is transmitted sequentially through the driving main gear 300, the driven main gear 311, the transmission shaft a310, the sun gear 312 of the single-row double-stage planetary gear mechanism and the gear ring 315 of the single-row double-stage planetary gear mechanism, one path of power is transmitted to the sun gear 322 of the Ravigneaux planetary gear mechanism through the clutch shifting device a340 and the hollow shaft d320, the other path of power is transmitted to the outer planetary gear 324 of the Ravigneaux planetary gear mechanism through the clutch shifting device b350 and the hollow shaft e330, the two paths of power influence each other, the transmission mode of the Ravigneaux planetary gear mechanism is changed, and then the power is transmitted through the gear ring 325 and is output to the differential 390 of the vehicle through the outer gear 326. When the vehicle runs in the gear, the second electric machine runs reversely relative to the rotation direction of the input shaft 110, and works in a power generation mode, and the generated electric energy is stored in the battery to realize partial energy recovery.
4, gear 4: when the second electric machine is in an electromagnetic braking state, the clutch shifting device a340 is in a connected state but does not transmit power, and the other clutch shifting devices and the clutch 134 are in a disconnected state, the power input from the input shaft 110 is reduced in speed by the first planetary gear mechanism, and then is directly transmitted to the outer gear 326 through the hollow shaft a131 and the output driving gear 130 in sequence, and is output to the differential 390 of the vehicle through the outer gear 326.
5, gear: the clutch shifting device a340 and the clutch shifting device e380 are in a connected state, other clutch shifting devices and the clutch 134 are in a disconnected state, at this time, power input by the input shaft 110 is transmitted through the driving main gear 300, the driven main gear 311 and the transmission shaft a310 in sequence, one path of power is transmitted to the sun gear 312 of the single-row double-stage planetary gear mechanism, the gear ring 315 of the single-row double-stage planetary gear mechanism, the clutch shifting device a340 and the hollow shaft d320, the other path of power is transmitted to the sun gear 322 of the Ravigneaux planetary gear mechanism through the clutch shifting device e380, the two paths of power influence each other, the transmission mode of the Ravigneaux planetary gear mechanism is changed, and the power is transmitted through the gear ring 325 and is output to the differential 390 of the vehicle through the outer gear 326. When the vehicle runs in the gear, the second motor runs in the same direction relative to the rotation direction of the input shaft 110, and plays a role in auxiliary driving.
6, gear 6: the clutches 134 are all connected to transmit power, the clutch shift device e380 is connected but not transmitting power, and the other clutch shift devices are all disconnected, and at this time, power input from the input shaft 110 is directly transmitted to the hollow shaft a131, and then transmitted to the outer gear 326 via the output drive gear 130, and then output to the differential 390 of the vehicle from the outer gear 326. At this time, the second motor operates in the same direction with respect to the rotation direction of the input shaft 110, and plays a role of auxiliary driving.
7, gear: the clutch shifting device b350 and the clutch shifting device e380 are in a connected state, other clutch shifting devices and the clutch 134 are in a disconnected state, at this time, power input by the input shaft 110 is transmitted through the driving main gear 300, the driven main gear 311 and the transmission shaft a310 in sequence, one path of power is transmitted to the outer planetary gear 324 of the Ravigneaux planetary gear mechanism through the sun gear 312 of the single-row double-stage planetary gear mechanism, the gear ring 315 of the single-row double-stage planetary gear mechanism, the clutch shifting device b350 and the hollow shaft e330, the other path of power is transmitted to the planet carrier 323 of the Ravigneaux planetary gear mechanism through the clutch shifting device e380, the two paths of power are mutually influenced, the transmission mode of the Ravigneaux planetary gear mechanism is changed, and then the power is transmitted through the gear ring 325 and is output to the differential 390 of the vehicle through the outer gear 326. When the vehicle runs in the gear, the second motor runs in the same direction relative to the rotation direction of the input shaft 110, and plays a role in auxiliary driving.
And 8, gear: the clutch shifting device c360 and the clutch shifting device e380 are connected, other clutch shifting devices and the clutch 134 are disconnected, at this time, power input by the input shaft 110 is transmitted to the planet carrier 323 of the ravigneaux type planetary gear mechanism through the clutch shifting device e380 after sequentially passing through the driving main gear 300, the driven main gear 311 and the transmission shaft a310, at this time, the connection of the clutch shifting device c360 brakes the hollow shaft e330 to restrain the outer planet gear 324 of the ravigneaux type planetary gear mechanism and change the transmission mode of the ravigneaux type planetary gear mechanism, and the transmitted power is transmitted through the ring gear 325 of the ravigneaux type planetary gear mechanism and is output to the differential 390 of the vehicle through the outer gear 326. When the vehicle runs in the gear, the second motor runs in the same direction relative to the rotation direction of the input shaft 110, and plays a role in auxiliary driving.
In this embodiment, the speed-changing and gear-shifting process of the automobile is realized by the switching of the connection and disconnection states of the clutch gear-shifting device and the clutch 134, and as can be seen from the above gear setting, when the gear 1 is shifted to the gear 5, the clutch gear-shifting device a340 is in the connection state, and the gear can be switched only by changing the connection and disconnection states of other clutch gear-shifting devices or the clutch 134, and the crossover gear-shifting can be realized; similarly, in the 5 th gear to the 8 th gear, the clutch shifting device e380 is always in a connected state, the gear switching can be realized only by changing the connection and disconnection states of other clutch shifting devices or the clutch 134, the gear shifting process is rapid and quick, and meanwhile, due to the arrangement of the core transmission component, the transmission can realize the functions of power shifting without being cut off and energy recovery and vehicle starting by adopting a two-way transmission mode when power is transmitted through the working process of the core transmission component.
Example 4:
another eight-speed horizontal type non-power-off automatic transmission is shown in fig. 6, the core transmission part of the eight-speed horizontal type non-power-off automatic transmission is shown in fig. 1, and a clutch 134 device is eliminated, the non-power-off automatic transmission structurally further comprises a shell, and a transmission shaft a310, a hollow shaft d320, a hollow shaft e330, a ravigneaux planetary gear mechanism and a single-row two-stage planetary gear mechanism are arranged in the shell; the transmission shaft a310, the hollow shaft d320 and the hollow shaft e330 are concentrically arranged, the transmission shaft a310 penetrates through the hollow shaft d320, and the hollow shaft d320 penetrates through the hollow shaft e 330; one end of the transmission shaft a310 is fixedly sleeved with a driven main gear 311, the input shaft 110 is fixedly sleeved with a driving main gear 300, the driven main gear 311 is meshed with the driving main gear 300, the other end of the transmission shaft a310 is fixedly connected with a sun gear 312 of the single-row double-stage planetary gear mechanism, and a planet carrier 313 of the single-row double-stage planetary gear mechanism is fixedly connected with the shell; the hollow shaft d320 is fixedly connected with a sun gear 322 of the Ravigneaux type planetary gear mechanism, an outer gear 326 is sleeved outside a gear ring 325 of the Ravigneaux type planetary gear mechanism, an output driving gear 130 is fixedly sleeved on the hollow shaft a131, and the outer gear 326 is meshed with the output driving gear 130; a transmission gear a331 is fixedly arranged on the hollow shaft e330, a transmission gear b332 is coaxially and fixedly connected to an outer planetary gear 324 of the Ravigneaux planetary gear mechanism, and the transmission gear a331 is meshed with the transmission gear b 332; further comprising clutched shifting device a340, clutched shifting device b350, clutched shifting device c360, clutched shifting device d370, clutched shifting device e380 and clutched shifting device f 381; the clutch shifting device a340 is used for connecting or disconnecting the ring gear 315 of the single-row double-stage planetary gear mechanism with or from the hollow shaft d320, the clutch shifting device b350 is used for connecting or disconnecting the ring gear 315 of the single-row double-stage planetary gear mechanism with or from the hollow shaft e330, the clutch shifting device c360 is used for connecting or disconnecting the hollow shaft e330 with or from the housing, the clutch shifting device d370 is used for connecting or disconnecting the planet carrier 323 of the Ravigneaux planetary gear mechanism with or from the housing, the clutch shifting device e380 is used for connecting or disconnecting the planet carrier 323 of the Ravigneaux planetary gear mechanism with or from the transmission shaft a310, and the clutch shifting device f381 is used for connecting or disconnecting the hollow shaft d320 with or from the transmission shaft a 310.
Compared with the embodiment 3, the clutch 134 is omitted in the embodiment, and the clutch shifting device f381 for connecting or disconnecting the hollow shaft d320 and the transmission shaft a310 is additionally arranged, so that compared with the embodiment 3, the embodiment can obtain more matched speed ratio and transmission effect, and is more suitable for actual speed change requirements of vehicles such as cars and the like.
The gear positions of the automatic transmission of the embodiment are set as follows:
p gear: all the clutching and shifting devices are in an off state, the transmission shaft a310 is locked through a P gear (not shown), and the automobile is in a parking state.
N gear: all clutching shifters are off, and the external gear 326 for output is free, having no power output.
R gear: direct reverse gear output and electric reverse gear output are divided. In a conventional mode, the reverse gear is only a short distance, and the reverse gear is generally driven by a motor in a reverse direction to perform electric reverse gear. When the direct reverse output is performed, the clutch shift device b350 and the clutch shift device d370 are connected, and the other clutch shift devices are disconnected, and at this time, the power input from the input shaft 110 is transmitted sequentially through the driving main gear 300, the driven main gear 311, the transmission shaft a310, the sun gear 312 of the single-row two-stage planetary gear mechanism, the ring gear 315 of the single-row two-stage planetary gear mechanism, the clutch shift device b350, the hollow shaft e330, the outer planetary gear 324 of the ravigneaux planetary gear mechanism, and the ring gear 325 of the ravigneaux planetary gear mechanism, and then is output to the differential 390 of the vehicle through the outer gear 326.
The D gear comprises eight gears, and the power transmission of each gear is as follows:
1, gear 1: the clutch shifting device a340 and the clutch shifting device d370 are connected, and the other clutch shifting devices are all disconnected, so that the power input from the input shaft 110 is transmitted through the driving main gear 300, the driven main gear 311, the transmission shaft a310, the sun gear 312 of the single-row double-stage planetary gear mechanism, the ring gear 315 of the single-row double-stage planetary gear mechanism, the clutch shifting device a340, the hollow shaft d320, and the sun gear 322 of the ravigneaux planetary gear mechanism in sequence, and at this time, because the clutch shifting device d370 is connected, the carrier 323 of the ravigneaux planetary gear mechanism is fixed, and the transmitted power is freely transmitted to the ring gear 325 of the ravigneaux planetary gear mechanism and is output to the differential 390 of the vehicle through the outer gear 326. When the vehicle runs in the gear, the second electric machine runs reversely relative to the rotation direction of the input shaft 110, and works in a power generation mode, and the generated electric energy is stored in the battery to realize partial energy recovery.
2, gear: the clutch shifting device a340 and the clutch shifting device c360 are connected, while the other clutch shifting devices are disconnected, at this time, the power input by the input shaft 110 is transmitted through the driving main gear 300, the driven main gear 311, the transmission shaft a310, the sun gear 312 of the single-row double-stage planetary gear mechanism, the ring gear 315 of the single-row double-stage planetary gear mechanism, the clutch shifting device a340, the hollow shaft d320 and the sun gear 322 of the ravigneaux planetary gear mechanism in sequence, at this time, the hollow shaft e330 is fixed because the clutch shifting device c360 is connected, and further the outer planet gear 324 of the ravigneaux planetary gear mechanism is restrained, the transmission mode of the ravigneaux planetary gear mechanism is changed relative to the 1 st gear state, and finally the power is transmitted through the ring gear 325 in a new mode and is output to the differential 390 of the vehicle by the outer gear 326. When the vehicle runs in the gear, the second electric machine runs reversely relative to the rotation direction of the input shaft 110, and works in a power generation mode, and the generated electric energy is stored in the battery to realize partial energy recovery.
3, gear 3: the clutch shifting device a340 and the clutch shifting device b350 are in a connected state, other clutch shifting devices are in a disconnected state, at the moment, power input by the input shaft 110 is transmitted through the driving main gear 300, the driven main gear 311, the transmission shaft a310, the sun gear 312 of the single-row double-stage planetary gear mechanism and the gear ring 315 of the single-row double-stage planetary gear mechanism in sequence, one path of power is transmitted to the sun gear 322 of the Ravigneaux planetary gear mechanism through the clutch shifting device a340 and the hollow shaft d320, the other path of power is transmitted to the outer planetary gear 324 of the Ravigneaux planetary gear mechanism through the clutch shifting device b350 and the hollow shaft e330, the two paths of power are mutually influenced, the transmission mode of the Ravigneaux planetary gear mechanism is changed, and then the power is transmitted through the gear ring 325 and is output to the differential 390 of the vehicle through the outer gear 326. When the vehicle runs in the gear, the second electric machine runs reversely relative to the rotation direction of the input shaft 110, and works in a power generation mode, and the generated electric energy is stored in the battery to realize partial energy recovery.
4, gear 4: when the second electric machine is in an electromagnetic braking state, the clutch shifting device a340 is in a connected state but does not transmit power, and the other clutch shifting devices are all in a disconnected state, the power input from the input shaft 110 is reduced by the first planetary gear mechanism, and then is directly transmitted to the outer gear 326 by the hollow shaft a131 and the output driving gear 130 in sequence, and is output to the differential 390 of the vehicle by the outer gear 326.
5, gear: the clutch shifting device a340 and the clutch shifting device e380 are in a connected state, other clutch shifting devices are in a disconnected state, at this time, power input by the input shaft 110 is transmitted through the driving main gear 300, the driven main gear 311 and the transmission shaft a310 in sequence, one path of power is transmitted to the sun gear 312 of the single-row double-stage planetary gear mechanism, the gear ring 315 of the single-row double-stage planetary gear mechanism, the clutch shifting device a340 and the hollow shaft d320, and is transmitted to the sun gear 322 of the Ravigneaux planetary gear mechanism, the other path of power is transmitted to the planet carrier 323 of the Ravigneaux planetary gear mechanism through the clutch shifting device e380, the two paths of power influence each other, and after the transmission mode of the Ravigneaux planetary gear mechanism is changed, the power is transmitted through the gear ring 325 and is output to the differential 390 of the vehicle through the outer gear 326. When the vehicle runs in the gear, the second motor runs in the same direction relative to the rotation direction of the input shaft 110, and plays a role in auxiliary driving.
6, gear 6: the clutch shifting device f381 is in a connected state for power transmission, the clutch shifting device e380 is in a connected state but not for power transmission, and other clutch shifting devices are in a disconnected state, at this time, power input by the input shaft 110 is transmitted sequentially through the driving main gear 300, the driven main gear 311 and the transmission shaft a310, and then is directly transmitted to the hollow shaft d320 and the sun gear 322 of the ravigneaux type planetary gear mechanism through the clutch shifting device f381, and is transmitted through the ravigneaux type planetary gear mechanism, and then is output to the differential 390 of the vehicle through the outer gear 326 on the gear ring 325.
7, gear: the clutch shifting device b350 and the clutch shifting device e380 are in a connected state, other clutch shifting devices are in a disconnected state, at the moment, power input by the input shaft 110 is transmitted through the driving main gear 300, the driven main gear 311 and the transmission shaft a310 in sequence, one path of power is transmitted to the outer planetary gear 324 of the Ravigneaux planetary gear mechanism through the sun gear 312 of the single-row double-stage planetary gear mechanism, the gear ring 315 of the single-row double-stage planetary gear mechanism, the clutch shifting device b350 and the hollow shaft e330, the other path of power is transmitted to the planet carrier 323 of the Ravigneaux planetary gear mechanism through the clutch shifting device e380, the two paths of power are mutually influenced, the transmission mode of the Ravigneaux planetary gear mechanism is changed, and then the power is transmitted through the gear ring 325 and is output to the differential 390 of the vehicle through the outer gear 326. When the vehicle runs in the gear, the second motor runs in the same direction relative to the rotation direction of the input shaft 110, and plays a role in auxiliary driving.
And 8, gear: the clutch shifting device c360 and the clutch shifting device e380 are connected, other clutch shifting devices are disconnected, at this time, power input by the input shaft 110 is transmitted to the planet carrier 323 of the Ravigneaux planetary gear mechanism through the clutch shifting device e380 after sequentially passing through the driving main gear 300, the driven main gear 311 and the transmission shaft a310, at this time, the connection of the clutch shifting device c360 brakes the hollow shaft e330 to restrain the outer planet gear 324 of the Ravigneaux planetary gear mechanism and change the transmission mode of the Ravigneaux planetary gear mechanism, and the transmitted power is transmitted through the gear ring 325 of the Ravigneaux planetary gear mechanism and is output to the differential 390 of the vehicle through the outer gear 326. When the vehicle runs in the gear, the second motor runs in the same direction relative to the rotation direction of the input shaft 110, and plays a role in auxiliary driving.
In this embodiment, the speed-changing and gear-shifting process of the automobile is realized by switching the connection and disconnection states of the clutch and gear-shifting devices, and as can be seen from the above gear settings, the clutch and gear-shifting device a340 is in the connection state from 1 gear to 5 gears, and the gear switching can be realized only by changing the connection and disconnection states of other clutch and gear-shifting devices, and the crossover gear shifting can be realized; similarly, in the 5 th gear to the 8 th gear, the clutch gear-shifting device e380 is always in a connected state, the gear can be switched only by changing the connection and disconnection states of other clutch gear-shifting devices, the gear-shifting process is rapid and quick, and meanwhile, due to the arrangement of the core transmission component, the transmission can realize the functions of power gear shifting without being cut off and energy recovery and vehicle starting by adopting a two-way transmission mode when power is transmitted through the working process of the core transmission component.
The foregoing is illustrative of the preferred embodiments of this invention, and it is to be understood that the invention is not limited to the precise form disclosed herein and that various other combinations, modifications, and environments may be resorted to, falling within the scope of the concept as disclosed herein, either as described above or as apparent to those skilled in the relevant art. And that modifications and variations may be effected by those skilled in the art without departing from the spirit and scope of the invention as defined by the appended claims.
Claims (2)
1. A non-power-off shift automatic transmission is characterized in that,
the planetary gear set comprises an input shaft (110), a transmission shaft (120), a first planetary gear mechanism, a second planetary gear mechanism, a first motor and a second motor; the input shaft (110) is used for driving the gear ring (141) of the first planetary gear mechanism to rotate, and the sun gear (143) of the first planetary gear mechanism is used for driving the transmission shaft (120) to rotate; the planet carrier (142) of the first planetary gear mechanism is used for driving the planet carrier (152) of the second planetary gear mechanism to rotate synchronously; a sun gear (153) of the second planetary gear mechanism is fixedly connected with a rotor (171) of the first motor, the transmission shaft (120) is connected with a rotor (181) of the second motor, and a stator (172) of the first motor and a stator (182) of the second motor are both fixedly connected with a gear ring (151) of the second planetary gear mechanism;
the planetary gear set further comprises a clutch (134), wherein the clutch (134) is used for realizing disconnection or driving connection of the planet carrier (142) of the first planetary gear mechanism and a transmission shaft (120);
the hollow shaft a (131) and the hollow shaft b (132) are also included; the transmission shaft (120), the hollow shaft a (131), the hollow shaft b (132), the sun gear (143) of the first planetary gear mechanism and the sun gear (153) of the second planetary gear mechanism are all arranged concentrically; the sun gear (143) of the first planetary gear mechanism is fixedly sleeved on the transmission shaft (120), and two ends of the hollow shaft a (131) are respectively and fixedly connected with the planet carrier (142) of the first planetary gear mechanism and the planet carrier (152) of the second planetary gear mechanism; the hollow shaft b (132) is rotatably sleeved on the transmission shaft (120), and a sun gear (153) of the second planetary gear mechanism and a rotor (171) of the first motor are fixedly sleeved on the hollow shaft b (132);
the device also comprises a flange a (191) and a motor base (193); one end of the input shaft (110) is fixedly connected with a gear ring (141) of the first planetary gear mechanism through a flange a (191); the motor base (193) is of a hollow structure, one end of the motor base (193) is fixedly connected with a gear ring (151) of the second planetary gear mechanism, the first motor and the second motor are plug-in motors, and the first motor and the second motor are fixedly installed in the motor base (193);
the planetary gear mechanism further comprises a shell, wherein a transmission shaft a (310), a hollow shaft d (320), a hollow shaft e (330), a Ravigneaux planetary gear mechanism and a single-row double-stage planetary gear mechanism are arranged in the shell;
the transmission shaft a (310), the hollow shaft d (320) and the hollow shaft e (330) are concentrically arranged, the transmission shaft a (310) penetrates through the hollow shaft d (320), and the hollow shaft d (320) penetrates through the hollow shaft e (330);
one end of the transmission shaft a (310) is fixedly sleeved with a driven main gear (311), the input shaft (110) is fixedly sleeved with a driving main gear (300), the driven main gear (311) is meshed with the driving main gear (300), the other end of the transmission shaft a (310) is fixedly connected with a sun gear (312) of the single-row double-stage planetary gear mechanism, and a planet carrier (313) of the single-row double-stage planetary gear mechanism is fixedly connected with the shell;
the hollow shaft d (320) is fixedly connected with a sun gear (322) of the Ravigneaux planetary gear mechanism, an external gear (326) is sleeved outside a gear ring (325) of the Ravigneaux planetary gear mechanism, an output driving gear (130) is fixedly sleeved on the hollow shaft a (131), and the external gear (326) is meshed with the output driving gear (130);
a transmission gear a (331) is fixedly arranged on the hollow shaft e (330), a transmission gear b (332) is coaxially and fixedly connected to an outer planet gear (324) of the Ravigneaux type planetary gear mechanism, and the transmission gear a (331) is meshed with the transmission gear b (332);
the gear shifting device comprises a clutch shifting device a (340), a clutch shifting device b (350), a clutch shifting device c (360), a clutch shifting device d (370) and a clutch shifting device e (380);
the clutch shifting device a (340) is used for connecting or disconnecting a gear ring (315) of the single-row double-stage planetary gear mechanism with or from the hollow shaft d (320), the clutch shifting device b (350) is used for connecting or disconnecting a gear ring (315) of the single-row double-stage planetary gear mechanism with or from the hollow shaft e (330), the clutch shifting device c (360) is used for connecting or disconnecting the hollow shaft e (330) with or from the housing, the clutch shifting device d (370) is used for connecting or disconnecting a planet carrier (323) of the Ravigneaux planetary gear mechanism with or from the housing, and the clutch shifting device e (380) is used for connecting or disconnecting the planet carrier (323) of the Ravigneaux planetary gear mechanism with or from the transmission shaft a (310).
2. A non-power-off shift automatic transmission is characterized in that,
the planetary gear set comprises an input shaft (110), a transmission shaft (120), a first planetary gear mechanism, a second planetary gear mechanism, a first motor and a second motor; the input shaft (110) is used for driving the gear ring (141) of the first planetary gear mechanism to rotate, and the sun gear (143) of the first planetary gear mechanism is used for driving the transmission shaft (120) to rotate; the planet carrier (142) of the first planetary gear mechanism is used for driving the planet carrier (152) of the second planetary gear mechanism to rotate synchronously; a sun gear (153) of the second planetary gear mechanism is fixedly connected with a rotor (171) of the first motor, the transmission shaft (120) is connected with a rotor (181) of the second motor, and a stator (172) of the first motor and a stator (182) of the second motor are both fixedly connected with a gear ring (151) of the second planetary gear mechanism;
the planetary gear set further comprises a clutch (134), wherein the clutch (134) is used for realizing disconnection or driving connection of the planet carrier (142) of the first planetary gear mechanism and a transmission shaft (120);
the hollow shaft a (131) and the hollow shaft b (132) are also included; the transmission shaft (120), the hollow shaft a (131), the hollow shaft b (132), the sun gear (143) of the first planetary gear mechanism and the sun gear (153) of the second planetary gear mechanism are all arranged concentrically; the sun gear (143) of the first planetary gear mechanism is fixedly sleeved on the transmission shaft (120), and two ends of the hollow shaft a (131) are respectively and fixedly connected with the planet carrier (142) of the first planetary gear mechanism and the planet carrier (152) of the second planetary gear mechanism; the hollow shaft b (132) is rotatably sleeved on the transmission shaft (120), and a sun gear (153) of the second planetary gear mechanism and a rotor (171) of the first motor are fixedly sleeved on the hollow shaft b (132);
the device also comprises a flange a (191) and a motor base (193); one end of the input shaft (110) is fixedly connected with a gear ring (141) of the first planetary gear mechanism through a flange a (191); the motor base (193) is of a hollow structure, one end of the motor base (193) is fixedly connected with a gear ring (151) of the second planetary gear mechanism, the first motor and the second motor are plug-in motors, and the first motor and the second motor are fixedly installed in the motor base (193);
the planetary gear mechanism further comprises a shell, wherein a transmission shaft a (310), a hollow shaft d (320), a hollow shaft e (330), a Ravigneaux planetary gear mechanism and a single-row double-stage planetary gear mechanism are arranged in the shell;
the transmission shaft a (310), the hollow shaft d (320) and the hollow shaft e (330) are concentrically arranged, the transmission shaft a (310) penetrates through the hollow shaft d (320), and the hollow shaft d (320) penetrates through the hollow shaft e (330);
one end of the transmission shaft a (310) is fixedly sleeved with a driven main gear (311), the input shaft (110) is fixedly sleeved with a driving main gear (300), the driven main gear (311) is meshed with the driving main gear (300), the other end of the transmission shaft a (310) is fixedly connected with a sun gear (312) of the single-row double-stage planetary gear mechanism, and a planet carrier (313) of the single-row double-stage planetary gear mechanism is fixedly connected with the shell;
the hollow shaft d (320) is fixedly connected with a sun gear (322) of the Ravigneaux planetary gear mechanism, an external gear (326) is sleeved outside a gear ring (325) of the Ravigneaux planetary gear mechanism, an output driving gear (130) is fixedly sleeved on the hollow shaft a (131), and the external gear (326) is meshed with the output driving gear (130);
a transmission gear a (331) is fixedly arranged on the hollow shaft e (330), a transmission gear b (332) is coaxially and fixedly connected to an outer planet gear (324) of the Ravigneaux type planetary gear mechanism, and the transmission gear a (331) is meshed with the transmission gear b (332);
the clutch gear shifting device comprises a clutch gear shifting device a (340), a clutch gear shifting device b (350), a clutch gear shifting device c (360), a clutch gear shifting device d (370), a clutch gear shifting device e (380) and a clutch gear shifting device f (381);
the clutch shifting device a (340) is used for connecting or disconnecting a ring gear (315) of the single-row double-stage planetary gear mechanism with or from the hollow shaft d (320), the clutch shifting device b (350) is used for connecting or disconnecting a ring gear (315) of the single-row double-stage planetary gear mechanism with or from the hollow shaft e (330), the clutch shifting device c (360) is used for connecting or disconnecting the hollow shaft e (330) with the housing, the clutch shifting device d (370) is used for connecting or disconnecting a planet carrier (323) of the Ravigneaux planetary gear mechanism with the shell, the clutch shifting device e (380) is used for connecting or disconnecting a planet carrier (323) of the Ravigneaux planetary gear mechanism with the transmission shaft a (310), the clutch shifting device f (381) is used for connecting or disconnecting the hollow shaft d (320) and the transmission shaft a (310).
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| DE102006056495A1 (en) * | 2006-02-06 | 2007-09-27 | Volkswagen Ag | Transmission for motor vehicle has planetary wheels of second group each with two different diameter axial sections that engage planetary wheels of first group with smaller diameter section and second sun wheel with larger diameter section |
| CN202165553U (en) * | 2011-06-30 | 2012-03-14 | 长城汽车股份有限公司 | Automatic transmission with eight forward gears and one reverse gear |
| DE102013110710A1 (en) * | 2012-10-22 | 2014-04-24 | Avl List Gmbh | Gearbox i.e. double planetary gearbox, for vehicle, has simple planetary gearset whose sun wheel is fixed to housing, and ravigneaux planetary gearset whose sun gear shaft is fixed to bar of simple planetary gearset |
| CN107160994A (en) * | 2016-03-07 | 2017-09-15 | 北京汽车动力总成有限公司 | A kind of stepless drive system of hybrid power electronics and automobile |
| CN107387687A (en) * | 2017-08-28 | 2017-11-24 | 无锡职业技术学院 | Based on lever method parallel connection compound planetary gearing |
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| US7179186B2 (en) * | 2005-01-04 | 2007-02-20 | General Motors Corporation | Electrically variable transmission having three interconnected planetary gear sets |
| US7329201B2 (en) * | 2005-08-03 | 2008-02-12 | Gm Global Technology Operations, Inc. | Electrically variable transmission having two or three planetary gear sets with two or three fixed interconnections |
| CA2810938C (en) * | 2012-03-26 | 2018-08-14 | Mcmaster University | Powertrain system for hybrid vehicles having compound and split modes of operation |
| CN113565936B (en) * | 2017-06-12 | 2022-07-15 | 沈长江 | Hybrid power mixing and parallel connection transformation type driving combination structure |
| DE102017222537A1 (en) * | 2017-12-12 | 2019-06-13 | Volkswagen Aktiengesellschaft | Drive arrangement for a hybrid vehicle |
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| DE102006056495A1 (en) * | 2006-02-06 | 2007-09-27 | Volkswagen Ag | Transmission for motor vehicle has planetary wheels of second group each with two different diameter axial sections that engage planetary wheels of first group with smaller diameter section and second sun wheel with larger diameter section |
| CN202165553U (en) * | 2011-06-30 | 2012-03-14 | 长城汽车股份有限公司 | Automatic transmission with eight forward gears and one reverse gear |
| DE102013110710A1 (en) * | 2012-10-22 | 2014-04-24 | Avl List Gmbh | Gearbox i.e. double planetary gearbox, for vehicle, has simple planetary gearset whose sun wheel is fixed to housing, and ravigneaux planetary gearset whose sun gear shaft is fixed to bar of simple planetary gearset |
| CN107160994A (en) * | 2016-03-07 | 2017-09-15 | 北京汽车动力总成有限公司 | A kind of stepless drive system of hybrid power electronics and automobile |
| CN107387687A (en) * | 2017-08-28 | 2017-11-24 | 无锡职业技术学院 | Based on lever method parallel connection compound planetary gearing |
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| CN111412253A (en) | 2020-07-14 |
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