CN110077212B - Pure electric double-shaft power coupling four-wheel drive system - Google Patents
Pure electric double-shaft power coupling four-wheel drive system Download PDFInfo
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- CN110077212B CN110077212B CN201910405259.7A CN201910405259A CN110077212B CN 110077212 B CN110077212 B CN 110077212B CN 201910405259 A CN201910405259 A CN 201910405259A CN 110077212 B CN110077212 B CN 110077212B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K1/00—Arrangement or mounting of electrical propulsion units
- B60K1/02—Arrangement or mounting of electrical propulsion units comprising more than one electric motor
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
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Abstract
The invention discloses a pure electric double-shaft power coupling four-wheel drive system which comprises a front shaft drive assembly, a rear shaft drive assembly and a central transmission shaft, wherein two ends of the central transmission shaft are respectively connected with the front shaft drive assembly and the rear shaft drive assembly so as to realize the mutual transmission of power between the front shaft drive assembly and the rear shaft drive assembly. The invention can be used for various four-wheel drive new energy automobiles driven by pure electric motors, such as luxury cars, off-road vehicles, engineering vehicles and the like. The pure electric double-shaft power coupling four-wheel drive system can be suitable for driving motors with the same or different power on front and rear shafts so as to realize power output under different working conditions. The invention adopts the special planetary gear, the power coupling transfer case and the main speed reducer to realize more than 10 driving modes such as single motor driving or double motor coupling driving so as to adapt to different vehicle driving working conditions, improve the motor driving efficiency, the whole vehicle dynamic property and the economy, and ensure the driving capability of the vehicle on a special road surface.
Description
Technical Field
The invention relates to the field of new energy automobile power systems, in particular to a pure electric double-shaft power coupling four-wheel drive system.
Background
With the development of society, automobiles have entered into thousands of households and become an indispensable transportation means for people to travel. Because the traditional internal combustion engine automobile continuously causes environmental pollution and the petroleum storage is increasingly scarce, the development of new energy automobiles has become an important direction of automobile development. At present, city development is rapid, most of vehicles are used in cities, and the conditions of automobiles in urban operation are stop-and-go and low speed, so that various working conditions exist.
The pure electric automobile has the advantages of zero emission, no pollution, low noise, high energy utilization rate, convenient maintenance and the like, is taken as an alternative scheme of the traditional automobile by a plurality of manufacturers, and most of driving motors of the pure electric automobile are matched by adopting peak power, especially four-wheel drive electric automobiles, the driving motor power design is generally more in allowance, and under the urban working condition, the motor is not required to output larger power, so that the waste of output power is caused, the power consumption is increased, and the endurance mileage is reduced. Therefore, various pure electric double-shaft driven four-wheel drive systems are proposed by many manufacturers, and the pure electric vehicles adopting the system realize power output to different working conditions through power matching of different drive motors of front shafts and rear shafts, but the four-wheel drive systems have the following problems: the front shaft and the rear shaft adopt 2 sets of motor driving systems which are separated, and although four-wheel drive can be realized, effective coupling output of double-motor power can not be realized under some special working conditions; when the front axle or the rear axle slips, the motor with the wheel slipping axle cannot output power; four-wheel drive cannot be realized when a certain drive motor of the front axle or the rear axle fails; the driving mode is single, and can not adapt to various driving conditions.
Disclosure of Invention
The invention aims to provide a pure electric double-shaft power coupling four-wheel drive system which can improve motor drive efficiency, whole vehicle power performance and economy and ensure the driving capability of a vehicle on a special road surface.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
a pure electric double-shaft power coupling four-wheel drive system comprises a front shaft drive assembly, a rear shaft drive assembly and a central transmission shaft, wherein two ends of the central transmission shaft are respectively connected with the front shaft drive assembly and the rear shaft drive assembly so as to realize the mutual transmission of power between the front shaft drive assembly and the rear shaft drive assembly;
the front axle driving assembly comprises a front driving motor A and a front driving assembly shell A, and a front planetary gear mechanism, a clutch C1, a brake B1 and a front main speed reduction mechanism are arranged in the front driving assembly shell A;
the front planetary gear mechanism comprises a sun gear A fixedly connected to an input shaft A, a planet carrier A is arranged on the input shaft A in a sleeved mode, a plurality of planetary gears A are arranged on the planet carrier A, the inner sides of the planetary gears A are respectively meshed with the sun gear A, and the outer sides of the planetary gears A are meshed with an outer gear ring A;
the front driving motor A is connected with an input shaft A where a sun gear A is positioned through a motor clutch A, one end of the input shaft A, which is close to the motor clutch A, is fixedly connected with an inner ring of a clutch C1, an outer ring of the clutch C1 is fixedly connected with a planet carrier A,
the inner ring of the brake B1 is fixedly connected with the outer edge of the outer ring gear A, and the outer ring of the brake B1 is fixedly connected on the front driving assembly shell;
the front driving assembly shell A is rotatably provided with a gear shaft A, and one end of the gear shaft A, which is close to the front wheel, is connected with a front main speed reduction mechanism;
the front driving assembly shell A is rotatably provided with a gear shaft A, one end of the gear shaft A, which is close to the front wheel, is connected with a front main speed reduction mechanism, and the front main speed reduction mechanism outputs power to a front left wheel and a front right wheel respectively;
a bevel gear A is fixedly connected on one side of the planet carrier A, the bevel gear A is sleeved on an input shaft A where the sun gear A is positioned in an empty mode,
the bevel gear A is connected with a front power coupling transfer mechanism, and the front power coupling transfer mechanism is respectively connected with one end, close to a front shaft driving assembly, of the gear shaft A and one end, close to a front shaft driving assembly, of the central transmission shaft;
the rear axle driving assembly comprises a rear driving motor B and a rear driving assembly shell, a rear planetary gear mechanism, a clutch C7, a brake B2 and a rear main speed reducing mechanism are arranged in the rear driving assembly shell,
the rear planetary gear mechanism comprises a sun gear B fixedly connected to an input shaft B, a planet carrier B is arranged on the input shaft B in a hollow sleeve mode, a plurality of planetary gears B are arranged on the planet carrier B, the inner sides of the planetary gears B are respectively meshed with the sun gear B, and the outer sides of the planetary gears B are meshed with an outer gear ring B;
the rear driving motor B is connected with an input shaft B where a sun gear B is positioned through a motor clutch B, one end of the input shaft B, which is close to the motor clutch B, is fixedly connected with an inner ring of a clutch C7, an outer ring of the clutch C7 is fixedly connected with a planet carrier B,
the inner ring of the brake B2 is fixedly connected with the outer edge of the outer ring B, and the outer ring of the brake B2 is fixedly connected on the rear driving assembly shell;
the front driving assembly shell B is rotatably provided with a gear shaft B, one end of the gear shaft B, which is close to the rear wheel, is connected with a rear main speed reduction mechanism, and the rear main speed reduction mechanism outputs power to the rear left wheel and the rear right wheel respectively;
a bevel gear B is fixedly connected on one side of the planet carrier B, the bevel gear B is sleeved on an input shaft B where the sun gear B is positioned,
the bevel gear B is connected with a rear power coupling transfer mechanism, and the rear power coupling transfer mechanism is respectively connected with one end, close to the rear shaft driving assembly, of the gear shaft B and the central transmission shaft.
Further, the front main speed reduction mechanism comprises a small bevel gear A and a large bevel gear A which are meshed with each other, the small bevel gear A is fixedly connected to one end, close to the front wheels, of the gear shaft A, a differential mechanism shell A is fixedly connected to the large bevel gear A, a differential mechanism A is installed in the differential mechanism shell A, a left side bevel gear of the differential mechanism A is connected with a front left half shaft, one side of the front left half shaft, close to the differential mechanism, is fixedly connected with an inner ring of a clutch C2, an outer ring of the clutch C2 is fixedly connected with the differential mechanism shell A, a right side bevel gear of the differential mechanism A is connected with a front right half shaft, power is output to the front left half shaft, and power is output to the front right half shaft.
Further, the rear main speed reduction mechanism comprises a small bevel gear B and a large bevel gear B which are meshed with each other, wherein the small bevel gear B is fixedly connected to one end, close to the rear wheels, of the gear shaft B, a differential mechanism shell B is fixedly connected to the large bevel gear B, a differential mechanism B is arranged in the differential mechanism shell B, a left side bevel gear of the differential mechanism B is connected with a rear left half shaft, one side, close to the differential mechanism, of the rear left half shaft is fixedly connected with an inner ring of a clutch C6, an outer ring of the clutch C6 is fixedly connected with the differential mechanism shell B, a right side bevel gear of the differential mechanism B is connected with a rear right half shaft, power is output to the rear left half shaft, and power is output to the rear right half shaft.
Further, the front power coupling transfer mechanism comprises a transfer case bevel gear A and a transfer case bevel gear B which are meshed with each other, the transfer case bevel gear A is meshed with the bevel gear A, the transfer case bevel gear A is sleeved on the gear shaft A in an empty mode, one side of the transfer case bevel gear A is fixedly connected with an outer ring of a clutch C3, and an inner ring of the clutch C3 is fixedly connected with the gear shaft A; the transfer case bevel gear B is sleeved on one end of the central transmission shaft close to the front shaft driving assembly in an empty mode, one side, close to the rear wheel direction, of the transfer case bevel gear B is fixedly connected with an outer ring of the clutch C4, and an inner ring of the clutch C4 is fixedly connected with the central transmission shaft.
Further, the rear power coupling transfer mechanism comprises a transfer case bevel gear C and a transfer case bevel gear D which are meshed with each other, the transfer case bevel gear C is meshed with the bevel gear B, the transfer case bevel gear C is sleeved on the gear shaft B in an empty mode, one side of the transfer case bevel gear C is fixedly connected with an outer ring of a clutch C5, and an inner ring of the clutch C5 is fixedly connected with the gear shaft B; the transfer case bevel gear D is fixedly connected to one end of the central transmission shaft, which is close to the rear shaft driving assembly.
Compared with the existing four-wheel drive system, the invention has the following advantages: (1) The front shaft and the rear shaft adopt the structures of a driving motor, a planetary gear mechanism, a power coupling transfer mechanism, a main speed reduction mechanism and the like, so that the front shaft and the rear shaft can be independently driven or driven in a power coupling way at the same time, and the front shaft and the rear shaft can be adapted to various different working conditions; (2) The designed power coupling transfer mechanism can realize independent driving and four-wheel driving of each shaft driving motor and power distribution, so that the whole vehicle controller can more reasonably use a driving mode and distribute power; (3) The pure electric double-shaft power coupling four-wheel drive system is provided with 16 drive modes, and comprises: front motor first gear, second gear front wheel drive, rear motor first gear, second gear rear wheel drive, front motor first gear four-wheel drive, front motor second gear four-wheel drive, rear motor first gear four-wheel drive, rear motor second gear four-wheel drive, double motor first gear four-wheel drive, double motor second gear four-wheel drive, double motor coupling first gear front wheel drive, double motor coupling first gear rear wheel drive and other 4 standby driving modes, the driving modes are many, and the adaptability to various working conditions is strong; (4) The pure electric double-shaft power coupling four-wheel drive system can use drive motors with the same power or different powers and is arranged on a front shaft or a rear shaft so as to output different powers under different working conditions, the motor power matching range is larger, the power consumption of the four-wheel drive electric automobile is reduced, and the cruising ability is improved.
Drawings
The invention is described in further detail below with reference to the attached drawings and detailed description:
FIG. 1 is a schematic diagram of the overall structure of a pure electric dual-shaft power coupling four-wheel drive system of the present invention;
FIG. 2 is a schematic diagram of the transmission of first gear driving power of the front drive motor A according to the present invention;
FIG. 3 is a schematic diagram of the transmission of drive power from the front drive motor A to the second gear;
FIG. 4 is a schematic diagram of a front drive motor A first gear four wheel drive power transfer according to the present invention;
FIG. 5 is a schematic diagram of a rear drive motor B first gear four wheel drive power transfer according to the present invention;
FIG. 6 is a schematic diagram of a two-motor, first gear four-wheel drive power transfer of the present invention;
fig. 7 is a schematic diagram of the power transmission of the dual-motor coupled first-gear front wheel drive of the present invention.
Detailed Description
As shown in fig. 1, the pure electric double-shaft power coupling four-wheel drive system comprises a front shaft drive assembly, a rear shaft drive assembly and a central transmission shaft 17, wherein two ends of the central transmission shaft are respectively connected with the front shaft drive assembly and the rear shaft drive assembly so as to realize the mutual transmission of power between the front shaft drive assembly and the rear shaft drive assembly;
the front axle driving assembly comprises a front driving motor A3 and a front driving assembly shell A5, and a front planetary gear mechanism, a clutch C11, a brake B118 and a front main speed reduction mechanism are arranged in the front driving assembly shell A5;
the front planetary gear mechanism comprises a sun gear A22 fixedly connected to an input shaft A, a planet carrier A21 is arranged on the input shaft A in a sleeved mode, a plurality of planetary gears A20 are arranged on the planet carrier A21, the inner sides of the planetary gears A20 are respectively meshed with the sun gear A22, and the outer sides of the planetary gears A20 are meshed with an outer gear ring A19;
the front driving motor A3 is connected with an input shaft A where a sun gear A22 is positioned through a motor clutch A2, one end of the input shaft A, which is close to the motor clutch A2, is fixedly connected with an inner ring of a clutch C11, an outer ring of the clutch C11 is fixedly connected with a planet carrier A21,
the inner ring of the brake B118 is fixedly connected with the outer edge of the outer ring gear A19, and the outer ring of the brake B118 is fixedly connected on the front driving assembly shell 5;
the front driving assembly shell A is rotatably provided with a gear shaft A12, and one end of the gear shaft A12, which is close to the front wheel, is connected with a front main speed reduction mechanism;
the front driving assembly shell A5 is rotatably provided with a gear shaft A12, one end of the gear shaft A12, which is close to the front wheels, is connected with a front main speed reduction mechanism, and the front main speed reduction mechanism outputs power to the front left wheels and the front right wheels respectively;
a bevel gear A23 is fixedly connected on one side of the planet carrier A21, the bevel gear A23 is sleeved on an input shaft A where a sun gear A22 is arranged,
the bevel gear A is connected with a front power coupling transfer mechanism, and the front power coupling transfer mechanism is respectively connected with one end, close to a front shaft driving assembly, of the gear shaft A and one end, close to a front shaft driving assembly, of the central transmission shaft;
the rear axle driving assembly comprises a rear driving motor B42 and a rear driving assembly shell 24, a rear planetary gear mechanism, a clutch C744, a brake B225 and a rear main speed reducing mechanism are arranged in the rear driving assembly shell 24,
the rear planetary gear mechanism comprises a sun gear B29 fixedly connected to an input shaft B, a planet carrier B28 is arranged on the input shaft B in a sleeved mode, a plurality of planetary gears B27 are arranged on the planet carrier B28, the inner sides of the planetary gears B27 are respectively meshed with the sun gear B29, and the outer sides of the planetary gears B27 are meshed with an outer gear ring B26;
the rear driving motor B42 is connected with an input shaft B where the sun gear B29 is positioned through a motor clutch B43, one end of the input shaft B, which is close to the motor clutch B43, is fixedly connected with the inner ring of a clutch C744, the outer ring of the clutch C744 is fixedly connected with the planet carrier B28,
the inner ring of the brake B225 is fixedly connected with the outer edge of the outer ring gear B26, and the outer ring of the brake B225 is fixedly connected on the rear driving assembly shell 24;
the front driving assembly shell B24 is rotatably provided with a gear shaft B34, one end of the gear shaft B34, which is close to the rear wheel, is connected with a rear main speed reduction mechanism, and the rear main speed reduction mechanism outputs power to the rear left wheel and the rear right wheel respectively;
a bevel gear B30 is fixedly connected on one side of the planet carrier B28, the bevel gear B30 is sleeved on an input shaft B where a sun gear B29 is positioned,
the bevel gear B30 is connected with a rear power coupling transfer mechanism, and the rear power coupling transfer mechanism is respectively connected with one end, close to the rear shaft driving assembly, of the gear shaft B and the central transmission shaft.
The front main speed reduction mechanism comprises a small bevel gear A11 and a large bevel gear A8 which are meshed with each other, the small bevel gear A is fixedly connected to one end of a gear shaft A, which is close to front wheels, the large bevel gear A8 is fixedly connected with a differential shell A6, a differential mechanism A7 is arranged in the differential shell A6, a left bevel gear of the differential mechanism A7 is connected with a front left half shaft 10, one side of the front left half shaft 10, which is close to the differential mechanism, is fixedly connected with an inner ring of a clutch C29, an outer ring of the clutch C29 is fixedly connected with the differential shell A6, a right bevel gear of the differential mechanism A7 is connected with a front right half shaft 4, the front left half shaft 10 outputs power to front left wheels, and the front right half shaft 4 outputs power to front right wheels.
The rear main speed reduction mechanism comprises a small bevel gear B35 and a large bevel gear B39 which are meshed with each other, the small bevel gear B35 is fixedly connected to one end, close to the rear wheels, of a gear shaft B34, a differential shell B38 is fixedly connected to the large bevel gear B39, a differential mechanism B40 is arranged in the differential shell B38, a left bevel gear of the differential mechanism B40 is connected with a rear left half shaft 36, one side, close to the differential mechanism, of the rear left half shaft 36 is fixedly connected with an inner ring of a clutch C637, an outer ring of the clutch C637 is fixedly connected with the differential shell B38, a right bevel gear of the differential mechanism B40 is connected with a rear right half shaft 41, the rear left half shaft 36 outputs power to the rear left wheels, and the rear right half shaft 41 outputs power to the rear right wheels.
The front power coupling transfer mechanism comprises a transfer case bevel gear A14 and a transfer case bevel gear B15 which are meshed with each other, the transfer case bevel gear A14 is meshed with the bevel gear A23, the transfer case bevel gear A14 is sleeved on the gear shaft A12 in an empty mode, one side of the transfer case bevel gear A14 is fixedly connected with an outer ring of a clutch C313, and an inner ring of the clutch C313 is fixedly connected with the gear shaft A12; the transfer case bevel gear B15 is sleeved on one end of the central transmission shaft 17 close to the front shaft driving assembly in an empty mode, one side, close to the rear wheel direction, of the transfer case bevel gear B15 is fixedly connected with an outer ring of a clutch C416, and an inner ring of the clutch C416 is fixedly connected with the central transmission shaft 17.
The rear power coupling transfer mechanism comprises a transfer case bevel gear C32 and a transfer case bevel gear D33 which are meshed with each other, the transfer case bevel gear C32 is meshed with the bevel gear B30, the transfer case bevel gear C32 is sleeved on the gear shaft B34 in an empty mode, one side of the transfer case bevel gear C32 is fixedly connected with an outer ring of a clutch C531, and an inner ring of the clutch C531 is fixedly connected with the gear shaft B34; the transfer case bevel gear D33 is fixedly connected to one end of the central transmission shaft 17, which is close to the rear axle driving assembly.
The gear shafts and the transmission shafts are arranged in the shell of the front and rear driving assemblies through corresponding bearings (not shown), and the clutches and the brakes in the driving assemblies are controlled by adopting hydraulic mechanisms (not shown).
The pure electric double-shaft power coupling four-wheel drive system has 16 drive modes in total, and the working principles of each drive motor, motor clutch and brake in a drive assembly in different working modes are shown in the following table 1:
table 1 working principle of each driving mode of pure electric double-shaft power coupling four-wheel driving system
The working principle of the invention is further described below with reference to typical working conditions in table 1:
as shown in fig. 2, the front motor is driven by a first gear front wheel under the light-load front-drive starting condition, at this time, the front driving motor A3 and the motor clutch A2 work to transmit power to the input shaft of the sun gear a22 of the front planetary gear mechanism of the front axle driving assembly, meanwhile, the brake B118 works to lock the external gear ring a19, and the clutch C313 works to combine the power of the transfer case helical gear a14 and the gear shaft a 12. At this time, the power output route: front drive motor A3, motor clutch A2, sun gear A22, planet carrier A21, bevel gear A23, transfer case bevel gear A14, gear shaft A12, small bevel gear A11, large bevel gear A8, differential case A6, differential mechanism A7, front right half shaft 4 and front left half shaft 10. At this time, the other gear sets are in an idle state, and the other brakes, clutches, rear drive motor B42, and motor clutch B43 are not operated. And the working principle of the first-gear rear wheel drive of the rear motor under the light-load rear-drive starting working condition is similar to that of the power transmission route.
As shown in fig. 3, the front motor is driven by a second-gear front wheel under the light-load front-drive driving condition, at this time, the front driving motor A3 and the motor clutch A2 work to transmit power to the input shaft of the sun gear a22 of the front planetary gear mechanism of the front axle driving assembly, and at the same time, the clutch C11 works to fixedly connect the input shaft of the sun gear a22 with the planet carrier a21 to directly transmit power. At this time, the power transmission route: front drive motor A3, motor clutch A2, sun gear A22, planet carrier A21, bevel gear A23, transfer case bevel gear A14, gear shaft A12, small bevel gear A11, large bevel gear A8, differential case A6, differential mechanism A7, front right half shaft 4 and front left half shaft 10. At this time, the other gear sets are in an idle state, and the other brakes, clutches, rear drive motor B42, and motor clutch B43 are not operated. And the working principle of the rear motor second gear rear wheel drive under the light load rear drive running condition is similar to that of the power transmission route.
As shown in fig. 4, under the light-load front motor four-drive starting condition, the front driving motor A3 and the motor clutch A2 work at this time to transmit power to the input shaft of the sun gear a22 of the front planetary gear mechanism of the front axle driving assembly, and meanwhile: brake B118 is operated to lock the outer ring gear a 19; clutch C313 works to power-couple transfer case helical gear a14 with gear shaft a 12; the clutch C416 works to fixedly connect the transfer case bevel gear B15 with the central transmission shaft 17 so as to realize power transmission to the rear shaft; the clutch C531 works to fixedly connect the transfer case bevel gear C32 with the gear shaft B34, so that power is transmitted to the rear main speed reducer. At this time, the power transmission route: after a front driving motor A3, a motor clutch A2, a sun gear A22, a planet carrier A21, a bevel gear A23 and a transfer case bevel gear A14, part of power is driven by the transfer case bevel gear A14, a gear shaft A12, a small bevel gear A11, a large bevel gear A8, a differential case A6, a differential mechanism A7, a front right half shaft 4 and a front left half shaft 10; the other part of power is driven by the transfer case bevel gear A14, the transfer case bevel gear B15, the central transmission shaft 17, the transfer case bevel gear D33, the transfer case bevel gear C32, the gear shaft B34, the small bevel gear B35, the large bevel gear B39, the differential case B38, the differential mechanism B40 and the rear right half shaft 41 and the rear left half shaft 36. At this time, the other gear sets are in idle state, and the other brakes and clutches are not operated. The working principle of the front motor secondary four-gear drive under the light-load front motor four-drive driving condition is similar to that of the power transmission route of fig. 3 and 4, and the rear driving force transmission route of fig. 4 is added on the basis of fig. 3.
As shown in fig. 5, in the light-load rear motor four-drive starting condition, the rear driving motor B42 and the motor clutch B43 work at this time, and power is transmitted to the input shaft of the sun gear B29 of the rear planetary gear mechanism of the rear axle driving assembly, and meanwhile: brake B225 is operated to lock the outer ring gear B26; the clutch C531 works to fixedly connect the transfer case helical gear C32 with the gear shaft B34; the clutch C416 works to fixedly connect the transfer case bevel gear B15 with the central transmission shaft 17 so as to realize power transmission to the front shaft; the clutch C313 works to combine the power of the transfer case bevel gear A14 and the power of the gear shaft A12, so that the power is transmitted to the front main speed reducer. At this time, the power transmission route: after a rear driving motor B3, a motor clutch B43, a sun gear B29, a planet carrier B28, a bevel gear B30 and a transfer case bevel gear C32, part of power is driven by the transfer case bevel gear C32, a gear shaft B34, a small bevel gear B35, a large bevel gear B39, a differential case B38, a differential mechanism B40, a rear right half shaft 41 and a rear left half shaft 36; the other part of power is driven by the transfer case bevel gear C32, the transfer case bevel gear D33, the central transmission shaft 17, the transfer case bevel gear B15, the transfer case bevel gear A14, the gear shaft A12, the small bevel gear A11, the large bevel gear A8, the differential case A6, the differential mechanism A7 and the front right half shaft 4 and the front left half shaft 10. At this time, the other gear sets are in idle state, and the other brakes and clutches are not operated. The working principle of the second-gear four-wheel drive of the rear motor under the light-load rear motor four-wheel drive driving condition is similar to that of the power transmission route of fig. 5, and only the first gear of the planetary gear is changed into the second gear.
As shown in fig. 6, under the heavy-duty four-wheel drive starting condition, the dual-motor first-gear four-wheel drive is implemented by: the front driving motor A3 and the motor clutch A2 work to transmit power to the input shaft of the sun gear A22 of the front planetary gear mechanism of the front shaft driving assembly, the brake B118 works to lock the outer gear ring A19, and the clutch C313 works to combine the power of the transfer case helical gear A14 and the power of the gear shaft A12. At this time, the power output route: front drive motor A3, motor clutch A2, sun gear A22, planet carrier A21, bevel gear A23, transfer case bevel gear A14, gear shaft A12, small bevel gear A11, large bevel gear A8, differential case A6, differential mechanism A7, front right half shaft 4 and front left half shaft 10. For the rear axle: at this time, the rear drive motor B42 and the motor clutch B43 operate to transmit power to the input shaft of the sun gear B29 of the rear planetary gear mechanism of the rear axle drive assembly, while: brake B225 is operated to lock the outer ring gear B26; the clutch C531 works to fixedly connect the transfer case helical gear C32 with the gear shaft B34; and the power is transmitted to the rear main speed reducer. At this time, the power transmission route: rear drive motor B3→motor clutch B43→sun gear B29→planet carrier B28→bevel gear B30→transfer case bevel gear C32→gear shaft B34→small bevel gear B35→large bevel gear B39→differential case B38→differential case B40→rear right half shaft 41 and rear left half shaft 36 to realize rear drive. At this time, other gear sets are in idle state, other brakes and clutches do not work, and the front and rear drive motors can avoid inconsistent rotation speeds of front and rear shafts under four-wheel drive only by the speed regulation of the controller.
As shown in fig. 7, when the rear axle is slipped under heavy load, the front wheel is driven by a first gear of front wheel coupling through a double motor, at this time, the front driving motor A3 works with the motor clutch A2 to transmit power to the input axle of the sun wheel a22 of the front planetary gear mechanism of the front axle driving assembly, meanwhile, the brake B118 works to lock the outer gear ring a19, and the clutch C313 works to combine the power of the transfer case bevel gear a14 with the power of the gear shaft a 12; simultaneously, the rear driving motor B42 and the motor clutch B43 work to transmit power to the input shaft of the sun gear B29 of the rear planetary gear mechanism of the rear shaft driving assembly, and simultaneously: the clutch C416 works to fixedly connect the transfer case bevel gear B15 with the central transmission shaft 17, so that power is transmitted to the front shaft. At this time, the power output route: front motor power comprises a front driving motor A3, a motor clutch A2, a sun gear A22, a planet carrier A21, a bevel gear A23 and a transfer case bevel gear A14; the rear motor power comprises a rear driving motor B3, a motor clutch B43, a sun gear B29, a planet carrier B28, a bevel gear B30, a transfer case bevel gear C32, a transfer case bevel gear D33, a central transmission shaft 17, a transfer case bevel gear B15 and a transfer case bevel gear A14; the power of the front and rear motors is coupled at the transfer case bevel gear A14 and is transmitted to the gear shaft A12→the small bevel gear A11→the large bevel gear A8→the differential case A6→the differential A7→the front right half shaft 4 and the front left half shaft 10, so that the double-motor coupling first-gear front wheel drive is realized. At this time, the other gear sets are in idle state, and the other brakes and clutches are not operated. And the working principle of the double-motor coupling first-gear rear wheel drive is similar to that of the power transmission route under the starting condition of the rear wheel when the heavy-load front axle slips.
The principle of operation of the standby mode is similar to that of each of the typical conditions described above.
In addition to the above working conditions, when the four-wheel drive system encounters a wheel slip on one side of the front axle, the front axle drive system can control the clutch C29 to work, so that the differential case A6 is fixedly connected with the front left half axle 10, namely, the differential A7 does not work, and the rotation speeds of the left and right front wheels are equal, so that the front axle can prevent the slip; similarly, when one side of the rear axle is slipping, the rear axle drive system may control clutch C637 to operate such that differential housing B38 is grounded to rear left axle shaft 36, i.e., such that differential B40 is not operating, and such that the left and right rear wheels are at equal speeds to prevent slipping of the rear axle.
Claims (3)
1. A pure electric double-shaft power coupling four-wheel drive system is characterized in that: the device comprises a front shaft driving assembly, a rear shaft driving assembly and a central transmission shaft, wherein two ends of the central transmission shaft are respectively connected with the front shaft driving assembly and the rear shaft driving assembly so as to realize the mutual transmission of power between the front shaft driving assembly and the rear shaft driving assembly;
the front axle driving assembly comprises a front driving motor A and a front driving assembly shell A, and a front planetary gear mechanism, a clutch C1, a brake B1 and a front main speed reduction mechanism are arranged in the front driving assembly shell A;
the front planetary gear mechanism comprises a sun gear A fixedly connected to an input shaft A, a planet carrier A is arranged on the input shaft A in a sleeved mode, a plurality of planetary gears A are arranged on the planet carrier A, the inner sides of the planetary gears A are respectively meshed with the sun gear A, and the outer sides of the planetary gears A are meshed with an outer gear ring A;
the front driving motor A is connected with an input shaft A where a sun gear A is positioned through a motor clutch A, one end of the input shaft A, which is close to the motor clutch A, is fixedly connected with an inner ring of a clutch C1, an outer ring of the clutch C1 is fixedly connected with a planet carrier A,
the inner ring of the brake B1 is fixedly connected with the outer edge of the outer ring gear A, and the outer ring of the brake B1 is fixedly connected on the front driving assembly shell;
the front driving assembly shell A is rotatably provided with a gear shaft A, and one end of the gear shaft A, which is close to the front wheel, is connected with a front main speed reduction mechanism;
the front driving assembly shell A is rotatably provided with a gear shaft A, one end of the gear shaft A, which is close to the front wheel, is connected with a front main speed reduction mechanism, and the front main speed reduction mechanism outputs power to a front left wheel and a front right wheel respectively;
a bevel gear A is fixedly connected on one side of the planet carrier A, the bevel gear A is sleeved on an input shaft A where the sun gear A is positioned in an empty mode,
the bevel gear A is connected with a front power coupling transfer mechanism, and the front power coupling transfer mechanism is respectively connected with one end, close to a front shaft driving assembly, of the gear shaft A and one end, close to a front shaft driving assembly, of the central transmission shaft;
the rear axle driving assembly comprises a rear driving motor B and a rear driving assembly shell, a rear planetary gear mechanism, a clutch C7, a brake B2 and a rear main speed reducing mechanism are arranged in the rear driving assembly shell,
the rear planetary gear mechanism comprises a sun gear B fixedly connected to an input shaft B, a planet carrier B is arranged on the input shaft B in a hollow sleeve mode, a plurality of planetary gears B are arranged on the planet carrier B, the inner sides of the planetary gears B are respectively meshed with the sun gear B, and the outer sides of the planetary gears B are meshed with an outer gear ring B;
the rear driving motor B is connected with an input shaft B where a sun gear B is positioned through a motor clutch B, one end of the input shaft B, which is close to the motor clutch B, is fixedly connected with an inner ring of a clutch C7, an outer ring of the clutch C7 is fixedly connected with a planet carrier B,
the inner ring of the brake B2 is fixedly connected with the outer edge of the outer ring B, and the outer ring of the brake B2 is fixedly connected on the rear driving assembly shell;
the front driving assembly shell B is rotatably provided with a gear shaft B, one end of the gear shaft B, which is close to the rear wheel, is connected with a rear main speed reduction mechanism, and the rear main speed reduction mechanism outputs power to the rear left wheel and the rear right wheel respectively;
a bevel gear B is fixedly connected on one side of the planet carrier B, the bevel gear B is sleeved on an input shaft B where the sun gear B is positioned,
the bevel gear B is connected with a rear power coupling transfer mechanism, and the rear power coupling transfer mechanism is respectively connected with one end, close to the rear shaft driving assembly, of the gear shaft B and the central transmission shaft;
the front main speed reduction mechanism comprises a small bevel gear A and a large bevel gear A which are meshed with each other, the small bevel gear A is fixedly connected to one end of a gear shaft A, which is close to front wheels, the large bevel gear A is fixedly connected with a differential case A, a differential mechanism A is installed in the differential case A, a left bevel gear of the differential mechanism A is connected with a front left half shaft, one side of the front left half shaft, which is close to the differential mechanism, is fixedly connected with an inner ring of a clutch C2, an outer ring of the clutch C2 is fixedly connected with the differential case A, a right bevel gear of the differential mechanism A is connected with a front right half shaft, the front left half shaft outputs power to front left wheels, and the front right half shaft outputs power to front right wheels;
the rear main speed reduction mechanism comprises a small bevel gear B and a large bevel gear B which are meshed with each other, wherein the small bevel gear B is fixedly connected to one end of a gear shaft B, which is close to a rear wheel, the large bevel gear B is fixedly connected with a differential mechanism shell B, a differential mechanism B is installed in the differential mechanism shell B, a left bevel gear of the differential mechanism B is connected with a rear left half shaft, one side of the rear left half shaft, which is close to the differential mechanism, is fixedly connected with an inner ring of a clutch C6, an outer ring of the clutch C6 is fixedly connected with the differential mechanism shell B, a right bevel gear of the differential mechanism B is connected with a rear right half shaft, power is output by the rear left half shaft to the rear left wheel, and power is output by the rear right half shaft to the rear right wheel.
2. An electric only dual axle power coupling four-wheel drive system as defined in claim 1, wherein: the front power coupling transfer mechanism comprises a transfer case bevel gear A and a transfer case bevel gear B which are meshed with each other, the transfer case bevel gear A is meshed with the bevel gear A, the transfer case bevel gear A is sleeved on the gear shaft A in an empty mode, one side of the transfer case bevel gear A is fixedly connected with an outer ring of a clutch C3, and an inner ring of the clutch C3 is fixedly connected with the gear shaft A; the transfer case bevel gear B is sleeved on one end of the central transmission shaft close to the front shaft driving assembly in an empty mode, one side, close to the rear wheel direction, of the transfer case bevel gear B is fixedly connected with an outer ring of the clutch C4, and an inner ring of the clutch C4 is fixedly connected with the central transmission shaft.
3. An electric only dual axle power coupling four-wheel drive system as defined in claim 1, wherein: the rear power coupling transfer mechanism comprises a transfer case bevel gear C and a transfer case bevel gear D which are meshed with each other, the transfer case bevel gear C is meshed with the bevel gear B, the transfer case bevel gear C is sleeved on the gear shaft B in an empty mode, one side of the transfer case bevel gear C is fixedly connected with an outer ring of a clutch C5, and an inner ring of the clutch C5 is fixedly connected with the gear shaft B; the transfer case bevel gear D is fixedly connected to one end of the central transmission shaft, which is close to the rear shaft driving assembly.
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| CN201910405259.7A CN110077212B (en) | 2019-05-16 | 2019-05-16 | Pure electric double-shaft power coupling four-wheel drive system |
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| CN201910405259.7A CN110077212B (en) | 2019-05-16 | 2019-05-16 | Pure electric double-shaft power coupling four-wheel drive system |
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| CN110077212B true CN110077212B (en) | 2024-04-05 |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100999190A (en) * | 2006-12-22 | 2007-07-18 | 吉林大学 | Biaxial four-wheel driven series type mixed power electric vehicle |
| DE102011056047A1 (en) * | 2011-12-05 | 2013-06-06 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Powertrain of a purely electric allradbetreibbaren motor vehicle |
| CN210234637U (en) * | 2019-05-16 | 2020-04-03 | 福建工程学院 | Pure electric double-shaft power coupling four-wheel drive system |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100999190A (en) * | 2006-12-22 | 2007-07-18 | 吉林大学 | Biaxial four-wheel driven series type mixed power electric vehicle |
| DE102011056047A1 (en) * | 2011-12-05 | 2013-06-06 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Powertrain of a purely electric allradbetreibbaren motor vehicle |
| CN210234637U (en) * | 2019-05-16 | 2020-04-03 | 福建工程学院 | Pure electric double-shaft power coupling four-wheel drive system |
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