CN112793414A - Two-gear speed change bridge driving system and vehicle - Google Patents

Two-gear speed change bridge driving system and vehicle Download PDF

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Publication number
CN112793414A
CN112793414A CN201911107493.8A CN201911107493A CN112793414A CN 112793414 A CN112793414 A CN 112793414A CN 201911107493 A CN201911107493 A CN 201911107493A CN 112793414 A CN112793414 A CN 112793414A
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CN
China
Prior art keywords
gear set
gear
clutch
drive system
planetary gear
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201911107493.8A
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Chinese (zh)
Inventor
栗娜
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to CN201911107493.8A priority Critical patent/CN112793414A/en
Publication of CN112793414A publication Critical patent/CN112793414A/en
Pending legal-status Critical Current

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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
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/12—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of electric gearing
    • 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
    • B60K17/02—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of clutch
    • 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
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
    • B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion

Abstract

The invention provides a two-gear speed change electric bridge driving system and a vehicle. The electric bridge driving system comprises two planetary gear sets and two clutches, the motor (E) is connected with a sun gear (11) of the first planetary gear set (10) and a sun gear (21) of the second planetary gear set (20), and a planet carrier (14) of the first planetary gear set (10) is connected with a ring gear (23) of the second planetary gear set (20); the outer hub of the first clutch (C1) is connected with the transmission housing, the inner hub of the first clutch (C1) is connected with the ring gear (13) of the first planetary gear set (10), the outer hub of the second clutch (C2) is connected with the transmission housing, and the inner hub of the second clutch (C2) is connected with the ring gear (23) of the second planetary gear set (20); the torque of the planet carrier (24) of the second planetary gear set (20) is transmitted to the differential (D). According to the two-gear speed change electric bridge driving system, transmission is stable in the gear shifting process, and the transmission system can be free of power interruption.

Description

Two-gear speed change bridge driving system and vehicle
Technical Field
The present invention relates to the field of motor vehicles, in particular to the field of transmissions for vehicles, in particular to an electric bridge driving system in a pure electric vehicle or a hybrid vehicle, and more particularly to a two-gear speed change electric bridge driving system and a vehicle comprising the electric bridge driving system.
Background
For electric vehicles, including pure electric vehicles and hybrid (hybrid electric vehicles), the electric driving mode includes two driving modes, namely central motor driving and hub motor driving. One common arrangement of a central motor drive system is also known as an electric bridge (eexle) drive system.
For a transmission of an electric vehicle that can provide two speed gears, one way of shifting is to shift gears using a synchronizer.
Fig. 1 is a schematic diagram of a bridge drive system for shifting gears using a synchronizer S. The rotor of the electric motor E is connected in a rotationally fixed manner (non-rotatably connected) to the motor shaft a1, and the motor shaft a1 is also connected in a rotationally fixed manner to the sun gear of the planetary gear set PG and to the gear Gt. The ring gear of the planetary gear set PG is fixed to the transmission case. Gear Gt is arranged in parallel with planetary gear set PG in the axial direction of motor shaft a 1. The engagement sleeve of the synchronizer S can be selectively connected to the gear Gt or to the planet carrier of the planetary gear set PG, so as to obtain two different gear ratios. The output torque of the engaging sleeve of the synchronizer S is transmitted to the gear shaft a2, and further transmitted to the differential D through gear transmission.
Disadvantages of this shifting scheme include:
(i) the motor shaft A1 is always connected with the sun gear and the gear Gt in the gear shifting process, the rotation of the motor E causes the gear shifting process to be not smooth enough, and the vibration of the motor E can influence the performance of a transmission system;
(ii) in the process of executing gear shifting by the synchronizer S, the power transmission is interrupted by firstly being put into a neutral gear, then a new gear can be put into the neutral gear, and the power of a transmission system is interrupted in the gear shifting process;
(iii) the power interruption of the gear shifting process results in a waste of battery power.
Disclosure of Invention
It is an object of the present invention to overcome or at least alleviate the above-identified deficiencies in the art described in the background and to provide a smooth-running electric bridge drive system capable of providing two-speed transmission and a vehicle comprising the same.
According to a first aspect of the present invention, there is provided a two-speed change bridge drive system comprising a transmission housing, an electric motor, a first planetary gear set, a second planetary gear set, a first clutch, a second clutch, a motor shaft and a differential, wherein,
the rotor of the electric motor is connected via the motor shaft in a rotationally fixed manner to the sun gear of the first planetary gear set and to the sun gear of the second planetary gear set,
the planet carrier of the first planetary gear set is connected in a rotationally fixed manner to the ring gear of the second planetary gear set;
the outer hub of the first clutch is connected in a rotationally fixed manner to the transmission housing, the inner hub of the first clutch is connected in a rotationally fixed manner to the ring gear of the first planetary gear set,
the outer hub of the second clutch is connected to the transmission housing in a rotationally fixed manner, and the inner hub of the second clutch is connected to the ring gear of the second planetary gear set in a rotationally fixed manner;
the torque of the carrier of the second planetary gear set is transmitted to the differential.
In at least one embodiment, the bridge drive system is in one gear when the inner and outer hubs of the first clutch are in an engaged state and the inner and outer hubs of the second clutch are in a disengaged state; the bridge drive system is in another gear when the inner and outer hubs of the first clutch are in a disengaged state and the inner and outer hubs of the second clutch are in an engaged state.
In at least one embodiment, the system further comprises a gear shaft and a reduction gear set,
the gear shafts are connected in a rotationally fixed manner to the carrier of the second planetary gear set and to one gear of the reduction gear set,
the differential housing of the differential is non-rotatably connected to another gear of the reduction gear set.
In at least one embodiment, the output half shaft of the differential is parallel to and offset from the motor shaft in the radial direction of the motor.
In at least one embodiment, the reduction gear set is a final gear set,
the terminal gear set comprises a terminal gear set driving wheel and a terminal gear set driven wheel which are meshed with each other,
one gear in the reduction gear set is the terminal gear set driving wheel, and the other gear in the reduction gear set is the terminal gear set driven wheel.
In at least one embodiment, the reduction gear set includes a first gear set, a second gear set, and an intermediate shaft,
the first gear set comprises a first gear set driving wheel and a first gear set driven wheel which are mutually meshed, the second gear set comprises a second gear set driving wheel and a second gear set driven wheel which are mutually meshed,
the first gear set driven wheel and the second gear set driving wheel are both arranged on the intermediate shaft in a non-relative rotation way,
one gear in the reduction gear set is the first gear set driving wheel, and the other gear in the reduction gear set is the second gear set driven wheel.
In at least one embodiment, a differential housing of the differential is connected in a rotationally fixed manner to the carrier of the second planetary gear set.
In at least one embodiment, the motor shaft is a hollow shaft, and one output half shaft of the differential passes through the motor shaft in the axial direction of the motor shaft.
In at least one embodiment, the electric machine is disposed inside the transmission housing.
According to a second aspect of the invention, a vehicle is provided comprising a battery for driving a rotor of the electric machine of the bridge drive system in rotation, and a two-speed electric bridge drive system according to the invention.
According to the two-gear speed change electric bridge driving system, transmission is stable in the gear shifting process, and the transmission system can be free of power interruption.
Drawings
FIG. 1 is a schematic diagram of a two-speed drive system for a two-speed electric bridge.
Fig. 2 is a schematic diagram of a two-speed power bridge drive system according to a first embodiment of the present invention.
Fig. 3 and 4 are schematic diagrams of the power transmission paths of the electric bridge drive system shown in fig. 2 in two different gears.
Fig. 5 is a schematic diagram of a two-speed power bridge drive system according to a second embodiment of the present invention.
Fig. 6 is a schematic diagram of a two-speed power bridge drive system according to a third embodiment of the present invention.
Description of the reference numerals
S, a synchronizer; a Gt gear; a PG planetary gear set; e, a motor; a differential mechanism D;
a1 motor shaft; a2 gear shaft; a3 intermediate shaft; a0 output half-shafts;
10 a first planetary gear set; 20 a second planetary gear set;
11. 21 a sun gear; 12. 22 planet wheels; 13. 23, a gear ring; 14. 24 a planet carrier;
g01 final gearset drive; g02 final gearset driven wheels;
g11 first gearset drive; g12 first gearset driven wheels; g21 second gear train drive wheel; g22 second gear set driven wheel;
axial direction A; r is radial.
Detailed Description
Exemplary embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood that the detailed description is intended only to teach one skilled in the art how to practice the invention, and is not intended to be exhaustive or to limit the scope of the invention.
Referring to fig. 2, unless otherwise noted, a represents an axial direction of the bridge drive system, which is coincident with an axial direction of the motor E, the first planetary gear set 10, the second planetary gear set 20, the first clutch C1, and the second clutch C2 in the bridge drive system; r denotes a radial direction of the bridge drive system, which is coincident with a radial direction of the motor E, the first planetary gear set 10, the second planetary gear set 20, the first clutch C1, and the second clutch C2 in the bridge drive system.
(first embodiment)
Referring first to fig. 2, a bridge driving system according to a first embodiment of the present invention will be described.
In this embodiment, the bridge drive system includes an electric machine E and a transmission system. The transmission system includes a first planetary gear set 10, a second planetary gear set 20, a first clutch C1, a second clutch C2, a motor shaft a1, a gear shaft a2, a final gear set, and a differential D.
Preferably, the electric machine E and the driveline are both disposed within a transmission housing (not shown).
The final gear set includes a final gear set drive pulley G01 and a final gear set driven pulley G02 that intermesh, and the number of teeth of the final gear set drive pulley G01 is less than the number of teeth of the final gear set drive pulley G02 (the radius of the final gear set drive pulley G01 is less than the radius of the final gear set driven pulley G02). Preferably, the final gearset driving pulley G01 and the final gearset driven pulley G02 are both spur gears (including helical and spur gears, preferably helical gears).
The motor E, the motor shaft a1, the gear shaft a2, the first clutch C1, the second clutch C2, the sun gear 11 of the first planetary gear set 10, the sun gear 21 of the second planetary gear set 20, and the final gear set drive G01 are coaxially arranged.
The final gearset driven wheels G02 and the two output half shafts of the differential D are coaxially disposed.
Preferably, the two output half shafts of the differential D are disposed parallel to the motor shaft A1, and in the radial direction R, the two output half shafts of the differential D are offset from the motor shaft A1.
The first planetary gear set 10 and the second planetary gear set 20 are arranged side by side in the axial direction a. The rotor of the electric machine E is connected in a rotationally fixed manner (non-rotatable manner) via a motor shaft a1 to the sun gear 11 of the first planetary gear set 10 and to the sun gear 21 of the second planetary gear set 20. Planet carrier 14 of the first planetary gear set 10 and
the ring gear 23 of the second planetary gear set 20 is connected in a rotationally fixed manner. It should be understood that carrier 14 and ring gear 23 may also be integrally formed, or ring gear 23 may be part of carrier 14.
The outer and inner hubs of the first clutch C1 (the two parts of the clutch that can be engaged or disengaged for transmitting or cutting off power) connect the transmission housing in a rotationally fixed manner to the ring gear 13 of the first planetary gear set 10. When the first clutch C1 is engaged, the ring gear 13 is connected in a rotationally fixed manner to the transmission housing; when in use
When the first clutch C1 is in the disengaged state, the ring gear 13 is able to rotate relative to the transmission housing.
The outer and inner hubs of the second clutch C2 are connected in a rotationally fixed manner to the transmission housing and to the ring gear 23 of the second planetary gear set 20. When the second clutch C2 is engaged, the ring gear 23 is connected in a rotationally fixed manner to the transmission housing; when the second clutch C2 is in the disengaged state, the ring gear 23 is able to rotate relative to the transmission housing.
The carrier 24 of the second planetary gear set 20 is connected in a rotationally fixed manner to a gear shaft a 2. An end of the gear shaft a2 in the axial direction a, which end is remote from the second planetary gearset 20, is provided with a final gearset driver G01. It should be appreciated that the planet carrier 24 may be integrally formed with the gear shaft a2, or the gear shaft a2 may be part of the planet carrier 24; the final gearset driver G01 may be integrally formed with the gear shaft a2, or the gear shaft a2 may be part of the final gearset driver G01.
The final gearset driven pulley G02 is non-rotatably connected to the differential housing of the differential D.
Next, the operation of the bridge drive system according to the present embodiment to realize two-speed gear shifting will be described with reference to fig. 3 and 4.
(i) The first clutch C1 is disengaged and the second clutch C2 is engaged
Referring to fig. 3, it is assumed that the inner hub of the first clutch C1 is disengaged from the outer hub and the inner hub of the second clutch C2 is engaged with the outer hub at this time.
In this case, the ring gear 23 is fixed and the ring gear 13 is not fixed. The power from the motor shaft a1 is input through the sun gear 21 of the second planetary gear set 20 and output through the planet carrier 24; while the ring gear 13 of the first planetary gear set 10 idles.
The power transmission path is as follows: the motor E, a motor shaft A1, a sun gear 21 of the second planetary gear set 20, planet gears 22, a planet carrier 24, a gear shaft A2, a terminal gear set driving wheel G01, a terminal gear set driven wheel G02 and a differential D.
(ii) The first clutch C1 is engaged and the second clutch C2 is disengaged
Referring to fig. 4, it is assumed that the inner hub of the first clutch C1 is engaged with the outer hub and the inner hub of the second clutch C2 is disengaged from the outer hub at this time.
At this time, the ring gear 13 is fixed, and the ring gear 23 is fixed to the carrier 14. The sun gear 11 of the first planetary gear set 10 inputs power, and the planet carrier 14 outputs power; the sun gear 21 and the ring gear 23 of the second planetary gear set 20 simultaneously input power, and the carrier 24 outputs power.
The torque transmission path is in turn: the motor E and the motor shaft A1 are respectively transmitted to the sun gear 11 and the sun gear 21; the power input by the sun gear 11 is transmitted to the ring gear 23 through the planetary gears 12 and the planet carrier 14, and then input to the planetary gears 22 as first power; the power input by the sun gear 21 is further transmitted to the planetary gears 22 as second power; the first power and the second power are transmitted to the planet wheels 22, are integrated and then are output to the gear shaft A2, the final gear set driving wheel G01, the final gear set driven wheel G02 and the differential D through the planet carrier 24.
(second embodiment)
Next, a bridge driving system according to a second embodiment of the present invention will be described with reference to fig. 5.
The second embodiment is a modification of the first embodiment. The second embodiment differs from the first embodiment mainly in that an intermediate shaft A3 is further provided downstream of the gear shaft a2, and the power output from the gear shaft a2 is transmitted to the differential D through a two-stage reduction gear set. By providing multiple reduction gear sets, a greater gear ratio is provided to the system.
The two-stage reduction gear set is a first gear set and a second gear set respectively. The first gearset includes a first gearset driving pulley G11 and a first gearset driven pulley G12, which are intermeshed, and the second gearset includes a second gearset driving pulley G21 and a second gearset driven pulley G22, which are intermeshed. The number of teeth of the first gear set driving wheel G11 is less than that of the first gear set driven wheel G12 (the radius of the first gear set driving wheel G11 is less than that of the first gear set driven wheel G12), and the number of teeth of the second gear set driving wheel G21 is less than that of the second gear set driven wheel G22 (the radius of the second gear set driving wheel G21 is less than that of the second gear set driven wheel G22). Preferably, the first and second gear sets are spur gear sets.
The gear shaft a2 is connected in a rotationally fixed manner to a first gearwheel drive G11, the first gearwheel driven wheel G12 and the second gearwheel drive G21 are each connected in a rotationally fixed manner to the countershaft A3, and the second gearwheel driven wheel G22 is connected in a rotationally fixed manner to the differential housing of the differential D.
(third embodiment)
Next, a bridge driving system according to a third embodiment of the present invention will be described with reference to fig. 6.
The third embodiment is a modification of the first embodiment. The third embodiment differs from the first embodiment primarily in that the output half shaft of the differential D is not offset in the radial direction R from the motor shaft a1, and the carrier 24 is directly connected to the differential case of the differential D without a fixed-axis reduction gear set disposed therebetween. It should be understood that the carrier 24 may be formed integrally with the differential case of the differential D, or the carrier 24 and the differential case may be rotationally fixedly connected by, for example, splines or the like.
In this embodiment, the rotational axes of the motor E, the motor shaft A1, the first clutch C1, the second clutch C2, the sun gear of the first planetary gear set 10, the sun gear of the second planetary gear set 20, and the output half shaft of the differential D are all the same.
The motor shaft a1 is a hollow rotating shaft. An output axle shaft A0 of the differential D passes through the motor shaft A1 in the axial direction A. This arrangement reduces the size of the electric drive system in the radial direction R.
The invention has at least one of the following advantages:
(i) the two clutches are used for realizing the two-gear speed change function, the synchronizers are not needed, and the transmission system can have no power interruption during the gear shifting process, for example, one clutch can be disengaged while the other clutch can be slowly engaged.
(ii) The clutch disengagement and engagement process is relatively smooth, which allows for smoother power transfer between the electric machine E and the transmission during gear shifting.
(iii) The clutch has an overload protection function, and when the transmitted torque is too large, the slip between the inner hub and the outer hub of the clutch can occur, so that the transmission system is protected from overload.
(iv) The transmission part of the electric bridge driving system has better performance in the aspects of Noise, Vibration and Harshness (NVH), and can prolong the service life of a vehicle.
Of course, the present invention is not limited to the above-described embodiments, and those skilled in the art can make various modifications to the above-described embodiments of the present invention without departing from the scope of the present invention under the teaching of the present invention.

Claims (10)

1. A two-speed bridge drive system comprises a transmission housing, an electric machine (E), a first planetary gear set (10), a second planetary gear set (20), a first clutch (C1), a second clutch (C2), a motor shaft (A1) and a differential (D), wherein,
the rotor of the electric machine (E) is connected in a rotationally fixed manner via the motor shaft (A1) to the sun gear (11) of the first planetary gear set (10) and to the sun gear (21) of the second planetary gear set (20),
the planet carrier (14) of the first planetary gear set (10) is connected in a rotationally fixed manner to the ring gear (23) of the second planetary gear set (20);
the outer hub of the first clutch (C1) is connected in a rotationally fixed manner to the transmission housing, the inner hub of the first clutch (C1) is connected in a rotationally fixed manner to the ring gear (13) of the first planetary gear set (10),
the outer hub of the second clutch (C2) is connected in a rotationally fixed manner to the transmission housing, and the inner hub of the second clutch (C2) is connected in a rotationally fixed manner to the ring gear (23) of the second planetary gear set (20);
the torque of the planet carrier (24) of the second planetary gear set (20) is transmitted to the differential (D).
2. The two-speed bridge drive system according to claim 1, wherein the bridge drive system is in one gear when the inner hub and the outer hub of the first clutch (C1) are in an engaged state and the inner hub and the outer hub of the second clutch (C2) are in a disengaged state; when the inner and outer hubs of the first clutch (C1) are in a disengaged state and the inner and outer hubs of the second clutch (C2) are in an engaged state, the bridge drive system is in another gear.
3. The two-speed, variable speed bridge drive system according to claim 1 or 2, further comprising a gear shaft (A2) and a reduction gear set,
the gear shafts (A2) are connected in a rotationally fixed manner to the planet carrier (24) of the second planetary gear set (20) and to a gear of the reduction gear set,
the differential housing of the differential (D) is connected in a rotationally fixed manner to a further gear of the reduction gear set.
4. The two-speed bridge drive system according to claim 3, wherein the output half-shaft of the differential (D) is parallel to and offset from the motor shaft (A1) in the radial direction (R) of the motor (E).
5. The two speed change bridge drive system according to claim 3, wherein the reduction gear set is a final gear set,
the final gear set comprises a final gear set driving wheel (G01) and a final gear set driven wheel (G02) which are meshed with each other,
the one gear of the reduction gear set is the final gear set drive wheel (G01), and the other gear of the reduction gear set is the final gear set driven wheel (G02).
6. The two-speed power bridge driving system according to claim 3, wherein the reduction gear set comprises a first gear set, a second gear set and an intermediate shaft (A3),
the first gear set comprises a first gear set driving wheel (G11) and a first gear set driven wheel (G12) which are meshed with each other, the second gear set comprises a second gear set driving wheel (G21) and a second gear set driven wheel (G22) which are meshed with each other,
the first gear set driven wheel (G12) and the second gear set driving wheel (G21) are both arranged on the intermediate shaft (A3) in a non-rotation way,
the one gear of the reduction gear set is the first gear set drive wheel (G11), and the other gear of the reduction gear set is the second gear set driven wheel (G22).
7. Two-speed bridge drive system according to claim 1 or 2, wherein a differential housing of the differential (D) is connected in a rotationally fixed manner to the planet carrier (24) of the second planetary gear set (20).
8. The two-speed bridge drive system according to claim 7, wherein the motor shaft (A1) is a hollow shaft, and one output half shaft (A0) of the differential (D) passes through the motor shaft (A1) in the axial direction (A) of the motor shaft (A1).
9. Two-speed bridge drive system according to claim 1 or 2, wherein the electric machine (E) is arranged inside the transmission housing.
10. Vehicle comprising a two-speed electrical bridge drive system according to any one of claims 1 to 9 and a battery for driving in rotation a rotor of the electric machine (E) of the electrical bridge drive system.
CN201911107493.8A 2019-11-13 2019-11-13 Two-gear speed change bridge driving system and vehicle Pending CN112793414A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201911107493.8A CN112793414A (en) 2019-11-13 2019-11-13 Two-gear speed change bridge driving system and vehicle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201911107493.8A CN112793414A (en) 2019-11-13 2019-11-13 Two-gear speed change bridge driving system and vehicle

Publications (1)

Publication Number Publication Date
CN112793414A true CN112793414A (en) 2021-05-14

Family

ID=75803264

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201911107493.8A Pending CN112793414A (en) 2019-11-13 2019-11-13 Two-gear speed change bridge driving system and vehicle

Country Status (1)

Country Link
CN (1) CN112793414A (en)

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