CN210234637U - 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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- CN210234637U CN210234637U CN201920704674.8U CN201920704674U CN210234637U CN 210234637 U CN210234637 U CN 210234637U CN 201920704674 U CN201920704674 U CN 201920704674U CN 210234637 U CN210234637 U CN 210234637U
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Abstract
The utility model discloses a pure electric biax power coupling four wheel drive system, it includes front axle drive assembly, rear axle drive assembly and central transmission shaft, and front axle drive assembly and rear axle drive assembly are connected respectively to the both ends of central transmission shaft to realize the mutual transmission of power between front axle drive assembly and the rear axle drive assembly. The utility model discloses can be used to all kinds of four-wheel drive new energy automobile that adopt pure electric motor drive, like luxury car, cross country vehicle, machineshop car etc.. The pure electric double-shaft power coupling four-wheel drive system can be suitable for driving motors with the same or different carrying powers on the front shaft and the rear shaft so as to realize power output under different working conditions. The utility model discloses a special planetary gear, power coupling transfer case and main reducer integral type design can realize that single motor drive or 10 remaining kinds of drive modes such as bi-motor coupling drive go the operating mode in order to adapt to different vehicles, improve motor drive efficiency, whole car dynamic property and economic nature to guarantee the driving force of vehicle on special road surface.
Description
Technical Field
The utility model relates to a new energy automobile driving system field especially relates to a pure electric biax power coupling four wheel drive system.
Background
With the development of society, automobiles have entered thousands of households, and become indispensable transportation tools for people to go out. Because the traditional internal combustion engine automobile continuously causes environmental pollution and the petroleum storage is increasingly in short supply, the development of new energy automobiles becomes an important direction for automobile development. At present, cities develop rapidly, most vehicles are used in the cities, and the running conditions of the vehicles in the cities are stop-and-go, low speed and various working conditions.
The pure electric vehicle has the advantages of zero emission, no pollution, low noise, high energy utilization rate, convenience in maintenance and the like, and is used as an alternative scheme of the traditional vehicle by a plurality of manufacturers, the driving motors of most pure electric vehicles are matched by adopting peak power, particularly, the driving motors of the four-wheel drive electric vehicles have more power design general allowances, and under urban working conditions, the motors are 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 provided by many manufacturers, and the pure electric vehicles adopting the system realize power output under different working conditions by matching the power of different driving motors of a front shaft and a rear shaft, but the four-wheel drive systems have the following problems: the front shaft and the rear shaft adopt 2 sets of separated motor driving systems, although four-wheel driving can be realized, effective coupling output of double-motor power cannot be realized under some special working conditions; when the front axle or the rear axle slips, the motor of the wheel slipping axle cannot output power; when a certain driving motor of the front axle or the rear axle fails, four-wheel drive cannot be realized; the driving mode is single, and the device cannot adapt to various driving conditions.
Disclosure of Invention
An object of the utility model is to provide a can improve motor drive efficiency, whole car dynamic property and economic nature to guarantee the electricelectric moves biax power coupling four wheel drive system of vehicle at the driving force on special road surface.
In order to achieve the above purpose, the utility model 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 shaft 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 reducing 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 sleeved on the input shaft A in a hollow mode, a plurality of planetary gears A are mounted 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 the sun gear A is positioned through a motor clutch A, one end of the input shaft A close to the motor clutch A is fixedly connected with an inner ring of a clutch C1, an outer ring of a 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 gear ring A, and the outer ring of the brake B1 is fixedly connected to the front drive assembly shell;
a gear shaft A is rotatably mounted in the front drive assembly shell A, and one end of the gear shaft A, which is close to the front wheel, is connected with a front main speed reducing mechanism;
a gear shaft A is rotatably mounted in the front drive assembly shell A, one end of the gear shaft A, which is close to the front wheel, is connected with a front main speed reducing mechanism, and the front main speed reducing mechanism respectively outputs power to a front left wheel and a front right wheel;
one side of the planet carrier A is fixedly connected with a bevel gear A, the bevel gear A is sleeved on the input shaft A where the sun gear A is positioned in an empty way,
the bevel gear A is connected with a front power coupling transfer mechanism which is respectively connected with the gear shaft A and one end of the central transmission shaft close to the front shaft driving assembly;
the rear shaft 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 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 sleeved on the input shaft B in a hollow mode, a plurality of planetary gears B are mounted 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 on which a sun gear B is arranged through a motor clutch B, one end of the input shaft B close to the motor clutch B is fixedly connected with an inner ring of a clutch C7, an outer ring of a 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 gear ring B, and the outer ring of the brake B2 is fixedly connected to the rear drive assembly shell;
a gear shaft B is rotatably mounted in the front drive assembly shell B, one end of the gear shaft B, which is close to the rear wheel, is connected with a rear main speed reducing mechanism, and the rear main speed reducing mechanism respectively outputs power to a rear left wheel and a rear right wheel;
one side of the planet carrier B is fixedly connected with a bevel gear B, the bevel gear B is sleeved on an input shaft B where the sun gear B is positioned in an empty way,
the bevel gear B is connected with a rear power coupling transfer mechanism, and the rear power coupling transfer mechanism is respectively connected with the gear shaft B and one end of the central transmission shaft close to the rear shaft driving assembly.
Furthermore, the front main reducing 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 wheel, of the gear shaft A, the large bevel gear A is fixedly connected with a differential shell A, a differential A is installed in the differential shell A, a left side bevel gear of the differential A is connected with a front left half shaft, one side, close to the differential, of the front left half shaft is fixedly connected with an inner ring of a clutch C2, an outer ring of the clutch C2 is fixedly connected with the differential shell A, a right side bevel gear of the differential A is connected with a front right half shaft, the front left half shaft outputs power to a front left wheel, and the front right half shaft outputs power.
Furthermore, the rear main reducing mechanism comprises a small bevel gear B and a large bevel gear B which are meshed with each other, the small bevel gear B is fixedly connected to one end, close to the rear wheel, of the gear shaft B, the large bevel gear B is fixedly connected with a differential case B, a differential B is installed in the differential case B, a left side bevel gear of the differential B is connected with a rear left half shaft, one side, close to the differential, 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 case B, a right side bevel gear of the differential B is connected with a rear right half shaft, the rear left half shaft outputs power to the rear left wheel, and the rear right half shaft outputs power.
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 a clutch C3 is fixedly connected with the gear shaft A; the transfer case bevel gear B is sleeved on one end, close to the front shaft driving assembly, of the central driving shaft in an empty mode, one side, close to the direction of the rear wheel, of the transfer case bevel gear B is fixedly connected with an outer ring of a clutch C4, and an inner ring of a clutch C4 is fixedly connected with the central driving 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 a clutch C5 is fixedly connected with the gear shaft B; and the transfer case bevel gear D is fixedly connected to one end of the central transmission shaft close to the rear shaft driving assembly.
The utility model discloses compare present four wheel drive system, have following advantage: (1) the front shaft and the rear shaft adopt structures such as a driving motor, a planetary gear mechanism, a power coupling transfer mechanism, a main speed reducing mechanism and the like, can realize independent driving or power coupling driving of the front shaft and the rear shaft at the same time, and can adapt 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 use a driving mode and distribute power more reasonably; (3) the pure electric double-shaft power coupling four-wheel drive system has 16 drive modes and comprises: the four-wheel drive system comprises a front motor first-gear and second-gear front wheel drive system, a rear motor first-gear and second-gear rear wheel drive system, a front motor first-gear four-wheel drive system, a front motor second-gear four-wheel drive system, a rear motor first-gear four-wheel drive system, a rear motor second-gear four-wheel drive system, a double-motor first-gear four-wheel drive system, a double-motor second-gear four-wheel drive system, a double-motor coupling first-gear front wheel drive system, a double-motor coupling first-gear rear wheel drive system and other 4 standby drive modes, a plurality of; (4) the pure electric double-shaft power coupling four-wheel drive system can use the drive motors with the same power or different powers and is arranged on the front shaft or the rear shaft, so that different powers can be output under different working conditions, the power matching range of the motor 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 following drawings and embodiments:
FIG. 1 is a schematic view of the overall structure of a pure electric double-shaft power coupling four-wheel drive system of the present invention;
fig. 2 is a schematic view of the front driving motor a of the present invention for transmitting the first gear driving power;
fig. 3 is a schematic diagram of the front driving motor a for transmitting the second-gear driving power;
fig. 4 is a schematic view of the front drive motor a of the present invention illustrating first-gear four-wheel drive power transmission;
fig. 5 is a schematic diagram of the rear drive motor B of the present invention for the first-gear four-wheel drive power transmission;
FIG. 6 is a schematic diagram of the dual-motor one-gear four-wheel drive power transmission of the present invention;
fig. 7 is a schematic view of the dual-motor coupling first-gear front wheel driving power transmission of the present invention.
Detailed Description
As shown in fig. 1, the pure electric dual-axle power coupling four-wheel drive system of the present invention comprises a front axle drive assembly, a rear axle drive assembly and a central transmission shaft 17, wherein two ends of the central transmission shaft are respectively connected to the front axle drive assembly and the rear axle drive assembly to realize the mutual transmission of power between the front axle drive assembly and the rear axle drive assembly;
the front axle driving assembly comprises a front driving motor A3 and a front driving assembly shell A5, wherein a front planetary gear mechanism, a clutch C11, a brake B118 and a front main speed reducing 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 mounted on the input shaft A in a hollow manner, a plurality of planetary gears A20 are mounted 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 located through a motor clutch A2, one end of the input shaft A close to the motor clutch A2 is fixedly connected with an inner ring of a clutch C11, an outer ring of a 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 gear ring A19, and the outer ring of the brake B118 is fixedly connected to the front drive assembly shell 5;
a gear shaft A12 is rotatably mounted in the front drive assembly shell A, and one end of the gear shaft A12 close to the front wheel is connected with the front main speed reducing mechanism;
a gear shaft A12 is rotatably mounted in the front drive assembly shell A5, one end of the gear shaft A12 close to the front wheel is connected with a front main speed reducing mechanism, and the front main speed reducing mechanism respectively outputs power to the front left wheel and the front right wheel;
one side of the planet carrier A21 is fixedly connected with a bevel gear A23, and the bevel gear A23 is sleeved on the input shaft A where the sun gear A22 is positioned,
the bevel gear A is connected with a front power coupling transfer mechanism which is respectively connected with the gear shaft A and one end of the central transmission shaft close to the front shaft driving assembly;
the rear shaft 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 mounted on the input shaft B in a hollow manner, a plurality of planetary gears B27 are mounted on a planet carrier B28, the inner sides of the planetary gears B27 are respectively meshed with a 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 on which a sun gear B29 is arranged through a motor clutch B43, one end of the input shaft B close to the motor clutch B43 is fixedly connected with an inner ring of a clutch C744, an outer ring of the clutch C744 is fixedly connected with a planet carrier B28,
the inner ring of the brake B225 is fixedly connected with the outer edge of the outer gear ring B26, and the outer ring of the brake B225 is fixedly connected to the rear drive assembly shell 24;
a gear shaft B34 is rotatably mounted in the front drive assembly shell B24, one end of the gear shaft B34 close to the rear wheel is connected with a rear main speed reducing mechanism, and the rear main speed reducing mechanism outputs power to the rear left wheel and the rear right wheel respectively;
one side of the planet carrier B28 is fixedly connected with a bevel gear B30, and the bevel gear B30 is freely 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 of the gear shaft B and one end of the central transmission shaft close to the rear shaft drive assembly.
The front main speed reducing 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, close to a front wheel, of a gear shaft A, the small bevel gear A8 is fixedly connected with a differential case A6, a differential case A6 is internally provided with a differential A7, a left bevel gear of a differential A7 is connected with a front left half shaft 10, one side, close to the differential, of the front left half shaft 10 is fixedly connected with an inner ring of a clutch C29, an outer ring of the clutch C29 is fixedly connected with a differential case A6, a right bevel gear of the differential A7 is connected with a front right half shaft 4, the front left half shaft 10 outputs power to the front left wheel, and the front right half shaft 4.
The rear main speed reducing 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 a rear wheel, of a gear shaft B34, the large bevel gear B39 is fixedly connected with a differential case B38, a differential case B40 is installed in the differential case B38, a left bevel gear on the left side of the differential case B40 is connected with a rear left half shaft 36, one side, close to the differential case, 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 a differential case B38, a right bevel gear on the right side of the differential case B40 is connected with a rear right half shaft 41, the rear left half shaft 36 outputs power to the.
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, wherein the transfer case bevel gear A14 is meshed with the bevel gear A23, the transfer case bevel gear A14 is sleeved on a 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 of the transfer case bevel gear B15 close to the direction of the rear wheel is fixedly connected with the outer ring of the clutch C416, and the 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, wherein the transfer case bevel gear C32 is meshed with a bevel gear B30, the transfer case bevel gear C32 is sleeved on a gear shaft B34 in an empty mode, one side of a 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 a gear shaft B34; the transfer case bevel gear D33 is fixedly connected to one end of the central transmission shaft 17 close to the rear axle drive assembly.
The gear shafts and the transmission shafts are arranged in the shell of the front and rear driving assembly through corresponding bearings (not shown in the figure), and the clutch and the brake in the driving assembly are controlled by a hydraulic mechanism (not shown in the figure).
The pure electric double-shaft power coupling four-wheel drive system has 16 drive modes in total, and the working principles of various drive motors, motor clutches, inner clutches of drive assemblies and brakes in different working modes are shown in table 1:
TABLE 1 working principle of all driving modes of pure electric double-shaft power coupling four-wheel driving system
The working principle of the present invention is further explained with respect to the typical working conditions in table 1 below:
as shown in fig. 2, the front motor is driven in first gear and front gear under the light-load front-wheel 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 shaft driving assembly, meanwhile, the brake B118 works to lock the outer gear ring a19, and the clutch C313 works to dynamically combine 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 → carrier a21 → helical gear a23 → transfer case helical gear a14 → gear shaft a12 → small bevel gear a11 → large bevel gear A8 → differential case a6 → differential a7 → front right and left half-shafts 4 and 10. At this time, the other gear sets are in an idling state, and the other brakes, clutches, rear drive motor B42, and motor clutch B43 are not operated. The working principle of the rear motor first-gear rear wheel drive under the light-load rear wheel drive starting working condition is similar to that of a power transmission route.
As shown in fig. 3, the front motor drives in two-gear front wheel mode under the light-load front-wheel-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 shaft driving assembly, and simultaneously, the clutch C11 works to fixedly connect the input shaft of the sun gear a22 and 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 → carrier a21 → helical gear a23 → transfer case helical gear a14 → gear shaft a12 → small bevel gear a11 → large bevel gear A8 → differential case a6 → differential a7 → front right and left half-shafts 4 and 10. At this time, the other gear sets are in an idling state, and the other brakes, clutches, rear drive motor B42, and motor clutch B43 are not operated. 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 a power transmission route.
As shown in fig. 4, under the light-load front motor four-wheel drive starting condition, the front motor four-wheel drive mode is adopted, at this time, the front drive motor A3 and the motor clutch a2 work, power is transmitted to the input shaft of the sun gear a22 of the front planetary gear mechanism of the front shaft drive assembly, and at the same time: the brake B118 works to lock the external gear ring A19; the clutch C313 works to dynamically combine the transfer case bevel gear A14 with the gear shaft A12; the clutch C416 works to fixedly connect the transfer case bevel gear B15 with the central transmission shaft 17 to realize the transmission of power 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 reducer. At this time, the power transmission route: front drive motor A3 → motor clutch a2 → sun gear a22 → carrier a21 → helical gear a23 → transfer case helical gear a14 rear, some of the power is forerunner via transfer case helical gear a14 → gear shaft a12 → small bevel gear a11 → large bevel gear A8 → differential case A6 → differential a7 → front right half-shaft 4 and front left half-shaft 10; the other part of the power realizes the rear-drive via the transfer gear helical gear a14 → the transfer gear helical gear B15 → the central transmission shaft 17 → the transfer gear helical gear D33 → the transfer gear helical gear C32 → the gear shaft B34 → the small bevel gear B35 → the large bevel gear B39 → the differential case B38 → the differential B40 → the rear right half shaft 41 and the rear left half shaft 36. At this time, the other gear sets are in an idling state, and the other brakes and clutches are not operated. The working principle of the front motor two-gear four-wheel drive under the light-load front motor four-wheel drive running condition is similar to the power transmission route of fig. 3 and 4, but the rear driving force transmission route in fig. 4 is added on the basis of fig. 3.
As shown in fig. 5, the rear motor four-wheel drive is in the rear motor first gear four-wheel drive under the light load rear motor four-wheel drive starting condition, at this time, the rear drive 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 drive assembly, and at the same time: the brake B225 works to lock the outer gear ring B26; the clutch C531 works to fixedly connect the transfer case bevel 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 to realize the transmission of power to the front shaft; the clutch C313 works to combine the power of the transfer case bevel gear A14 and the gear shaft A12 to realize the power transmission to the front main speed reducer. At this time, the power transmission route: the rear drive motor B3 → the motor clutch B43 → the sun gear B29 → the carrier B28 → the helical gear B30 → the transfer bevel gear C32, and a part of the power is driven by the transfer bevel gear C32 → the gear shaft B34 → the small bevel gear B35 → the large bevel gear B39 → the differential case B38 → the differential B40 → the rear right half shaft 41 and the rear left half shaft 36; another part of the power achieves forerunner via the transfer gear helical gear C32 → transfer gear helical gear D33 → central propeller shaft 17 → transfer gear helical gear B15 → transfer gear helical gear a14 → gear shaft a12 → bevel pinion a11 → bevel pinion A8 → differential case a6 → differential a7 → front right axle shaft 4 and front left axle shaft 10. At this time, the other gear sets are in an idling state, and the other brakes and clutches are not operated. The working principle of the rear motor two-gear four-wheel drive under the light-load rear motor four-wheel drive running condition is similar to 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, the dual-motor first-gear four-wheel drive under the heavy-load four-wheel drive starting condition is adopted, and at the moment: the front driving motor A3 works with a motor clutch A2, power is transmitted to an input shaft of a sun gear A22 of a front planetary gear mechanism of the front axle driving assembly, meanwhile, a brake B118 works to lock an outer gear ring A19, and a clutch C313 works to dynamically combine a transfer bevel gear A14 with a gear shaft A12. At this time, the power output route: front drive motor A3 → motor clutch a2 → sun gear a22 → carrier a21 → helical gear a23 → transfer case helical gear a14 → gear shaft a12 → small bevel gear a11 → large bevel gear A8 → differential case a6 → differential a7 → front right and left half-shafts 4 and 10. For the rear axle: at this time, the rear driving motor B42 and the motor clutch B43 work, power is transmitted to the input shaft of the sun gear B29 of the rear planetary gear mechanism of the rear shaft driving assembly, and simultaneously: the brake B225 works to lock the outer gear ring B26; the clutch C531 works to fixedly connect the transfer case bevel 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 → carrier B28 → helical gear B30 → transfer case helical gear C32 → gear shaft B34 → small bevel gear B35 → large bevel gear B39 → differential case B38 → differential B40 → rear right half shaft 41 and rear left half shaft 36 realize rear drive. At the moment, other gear sets are in an idle running state, other brakes and clutches do not work, and the front and rear driving motors can avoid the inconsistent rotating speeds of the front and rear shafts under four-wheel drive only through the speed regulation of the controller.
As shown in fig. 7, when the heavy-load rear axle slips, the starting working condition of the front wheel adopts dual-motor coupling first-gear front wheel drive, at this time, a front drive motor A3 and a motor clutch a2 work, power is transmitted to an input shaft of a sun gear a22 of a front planetary gear mechanism of the front axle drive assembly, meanwhile, a brake B118 works to lock an outer gear ring a19, and a clutch C313 works to dynamically combine a transfer case bevel gear a14 with a gear shaft a 12; meanwhile, the rear driving motor B42 works with the motor clutch B43, and transmits power to the input shaft of the sun gear B29 of the rear planetary gear mechanism of the rear axle driving assembly, and at the same time: the clutch C416 works to fixedly connect the transfer case bevel gear B15 with the central transmission shaft 17, so as to transmit power to the front shaft. At this time, the power output route: the front motor power is formed by a front driving motor A3 → a motor clutch A2 → a sun gear A22 → a planet carrier A21 → a bevel gear A23 → a transfer case bevel gear A14; the rear motor power is formed by 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 → a transfer case bevel gear A14; the power of the front and rear electric machines 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, and the double-motor coupling first-gear front wheel driving is realized. At this time, the other gear sets are in an idling state, and the other brakes and clutches are not operated. And the working principle of double-motor coupling one-gear rear wheel driving is adopted in the rear wheel starting working condition when the heavy-load front shaft slips, and the working principle is similar to the power transmission route.
The working principle of the standby mode is similar to that of the above-described respective typical operating conditions.
In addition to the above conditions, when the four-wheel drive system encounters wheel slip on one side of the front axle, the front axle drive system may control the operation of the clutch C29, so that the differential case a6 is fixedly connected with the front left half axle 10, i.e. the differential a7 is not operated, and the rotation speeds of the left and right front wheels are equal, so that the front axle can be prevented from slipping; similarly, when the wheels on one side of the rear axle slip, the rear axle drive system may control operation of clutch C637 to ground differential housing B38 to the rear left axle shaft 36, i.e., to deactivate differential B40 and equalize the rotational speeds of the left and right rear wheels so that the rear axle is prevented from slipping.
Claims (5)
1. The utility model provides a pure electric biax power coupling four wheel drive system which characterized in that: the transmission mechanism 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 shaft 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 reducing 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 sleeved on the input shaft A in a hollow mode, a plurality of planetary gears A are mounted 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 the sun gear A is positioned through a motor clutch A, one end of the input shaft A close to the motor clutch A is fixedly connected with an inner ring of a clutch C1, an outer ring of a 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 gear ring A, and the outer ring of the brake B1 is fixedly connected to the front drive assembly shell;
a gear shaft A is rotatably mounted in the front drive assembly shell A, one end of the gear shaft A, which is close to the front wheel, is connected with a front main speed reducing mechanism, and the front main speed reducing mechanism respectively outputs power to a front left wheel and a front right wheel;
one side of the planet carrier A is fixedly connected with a bevel gear A, the bevel gear A is sleeved on the input shaft A where the sun gear A is positioned in an empty way,
the bevel gear A is connected with a front power coupling transfer mechanism which is respectively connected with the gear shaft A and one end of the central transmission shaft close to the front shaft driving assembly;
the rear shaft 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 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 sleeved on the input shaft B in a hollow mode, a plurality of planetary gears B are mounted 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 on which a sun gear B is arranged through a motor clutch B, one end of the input shaft B close to the motor clutch B is fixedly connected with an inner ring of a clutch C7, an outer ring of a 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 gear ring B, and the outer ring of the brake B2 is fixedly connected to the rear drive assembly shell;
a gear shaft B is rotatably mounted in the front drive assembly shell B, one end of the gear shaft B, which is close to the rear wheel, is connected with a rear main speed reducing mechanism, and the rear main speed reducing mechanism respectively outputs power to a rear left wheel and a rear right wheel;
one side of the planet carrier B is fixedly connected with a bevel gear B, the bevel gear B is sleeved on an input shaft B where the sun gear B is positioned in an empty way,
the bevel gear B is connected with a rear power coupling transfer mechanism, and the rear power coupling transfer mechanism is respectively connected with the gear shaft B and one end of the central transmission shaft close to the rear shaft driving assembly.
2. A purely electric two-axle power-coupled four-wheel drive system according to claim 1, characterized in that: the front main reducing 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 wheel, of a gear shaft A, the large bevel gear A is fixedly connected with a differential shell A, a differential A is installed in the differential shell A, a left bevel gear of the differential A is connected with a front left half shaft, one side, close to the differential, of the front left half shaft is fixedly connected with an inner ring of a clutch C2, an outer ring of a clutch C2 is fixedly connected with the differential shell A, a right bevel gear of the differential A is connected with a front right half shaft, the front left half shaft outputs power to a front left wheel, and the front right half shaft outputs power.
3. A purely electric two-axle power-coupled four-wheel drive system according to claim 1, characterized in that: the rear main reducing mechanism comprises a small bevel gear B and a large bevel gear B which are meshed with each other, the small bevel gear B is fixedly connected to one end, close to a rear wheel, of a gear shaft B, the large bevel gear B is fixedly connected with a differential case B, a differential B is installed in the differential case B, a left side bevel gear of the differential B is connected with a rear left half shaft, one side, close to the differential, of the rear left half shaft is fixedly connected with an inner ring of a clutch C6, an outer ring of a clutch C6 is fixedly connected with the differential case B, a right side bevel gear of the differential B is connected with a right rear half shaft, the rear left half shaft outputs power to a rear left wheel, and the rear right half shaft.
4. A purely electric two-axle power-coupled four-wheel drive system according to claim 1, characterized in that: 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 the outer ring of a clutch C3, and the 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, close to the front shaft driving assembly, of the central driving shaft in an empty mode, one side, close to the direction of the rear wheel, of the transfer case bevel gear B is fixedly connected with an outer ring of a clutch C4, and an inner ring of a clutch C4 is fixedly connected with the central driving shaft.
5. A purely electric two-axle power-coupled four-wheel drive system according to claim 1, characterized in that: 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 a bevel gear B, the transfer case bevel gear C is sleeved on a 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 a clutch C5 is fixedly connected with the gear shaft B; and the transfer case bevel gear D is fixedly connected to one end of the central transmission shaft close to the rear shaft driving assembly.
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110077212A (en) * | 2019-05-16 | 2019-08-02 | 福建工程学院 | A kind of pure electric vehicle double-shaft power coupling four-wheel drive system |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110077212A (en) * | 2019-05-16 | 2019-08-02 | 福建工程学院 | A kind of pure electric vehicle double-shaft power coupling four-wheel drive system |
| CN110077212B (en) * | 2019-05-16 | 2024-04-05 | 福建工程学院 | Pure electric double-shaft power coupling four-wheel drive system |
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