CN112937272A - Two-gear speed change bridge driving system - Google Patents
Two-gear speed change bridge driving system Download PDFInfo
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- CN112937272A CN112937272A CN201911259793.8A CN201911259793A CN112937272A CN 112937272 A CN112937272 A CN 112937272A CN 201911259793 A CN201911259793 A CN 201911259793A CN 112937272 A CN112937272 A CN 112937272A
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- 230000008859 change Effects 0.000 title abstract description 10
- 230000005540 biological transmission Effects 0.000 claims abstract description 23
- 230000009977 dual effect Effects 0.000 claims abstract description 23
- 239000000126 substance Substances 0.000 claims 1
- 238000010586 diagram Methods 0.000 description 4
- 230000009467 reduction Effects 0.000 description 3
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000007812 deficiency Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
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Classifications
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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
-
- 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
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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
- B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
- B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
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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
- B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Electric Propulsion And Braking For Vehicles (AREA)
Abstract
The invention provides a two-gear speed-changing electric bridge driving system which comprises a motor (E), a motor shaft (Se) and a Double Clutch (DC), the dual clutch transmission comprises a plurality of gears, a planetary gear set (PG) and a differential (D), wherein a motor shaft (Se) is connected with a rotor of a motor (E) and a driving part of a Dual Clutch (DC), a first driven disc (C1) of the Dual Clutch (DC) is connected with one gear of the plurality of gears, a second driven disc (C2) of the Dual Clutch (DC) is connected with another gear of the plurality of gears, one gear is used for transmitting torque to a terminal gear of the plurality of gears through a first transmission path, the other gear is used for transmitting the torque to the terminal gear through a second transmission path, a sun gear (PG1) of the planetary gear set (PG) is connected with the terminal gear, and a planet carrier of the planetary gear set (PG) is connected with a shell of the differential (D). The two-gear speed change electric bridge driving system has compact structure and can realize higher transmission ratio by using smaller size.
Description
Technical Field
The invention relates to the field of motor vehicles, in particular to the field of transmissions of vehicles, in particular to an electric bridge driving system in a pure electric vehicle or a hybrid vehicle, and more particularly to an electric bridge driving system with two-gear speed change.
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.
Chinese patent publication CN109424717A discloses a two-speed transmission, an electric drive train and an electric vehicle, and as shown in fig. 1, an electric drive train (hereinafter also referred to as an electric bridge drive system) eA1 in the patent publication includes an electric motor E, a dual clutch DC, a first shaft S1, a second shaft S2, an intermediate shaft Sm, six gears for speed change, and a differential D.
The second shaft S2 is a hollow shaft, and the second shaft S2 is sleeved on the first shaft S1, and the two shafts can rotate relatively. The dual clutch DC comprises a drive part, which is connected rotationally fixed (non-rotatably) to the rotor of the electric machine E, a first driven disk C1, which is connected rotationally fixed to the first shaft S1, and a second driven disk C2, which is connected rotationally fixed to the second shaft S2, as well as a first driven disk C1. The first shaft S1 is also non-rotatably connected with the first gear G1 and the second shaft S2 is also non-rotatably connected with the second gear G2. The first gear G1 meshes with the third gear G3, and the second gear G2 meshes with the fourth gear G4. The third gear G3 and the fourth gear G4 are each connected in a rotationally fixed manner to an intermediate shaft Sm, which is also connected in a rotationally fixed manner to the fifth gear G5. The fifth gear G5 is connected to the sixth gear G6 in a rotationally fixed manner, and the sixth gear G6 is connected to the housing of the differential D in a rotationally fixed manner.
When the first driven disc C1 is engaged with the driving part of the dual clutch DC and the second driven disc C2 is disengaged from the driving part of the dual clutch DC, the bridge drive system eA1 is in the first speed gear; when the first driven disk C1 is disengaged from the driving part of the dual clutch DC and the second driven disk C2 is engaged with the driving part of the dual clutch DC, the bridge drive system eA1 is in the second speed gear.
Fig. 2 shows a schematic diagram of the bridge drive system eA1 viewed in the axial direction. In order to achieve the desired gear ratio, the third gear G3, the fourth gear G4, and the sixth gear G6 all need to have a large diameter, and the system needs to occupy a large space, particularly in the X direction and the Z direction in fig. 2. However, when the vehicle interior space is limited and the mounting space left for the transmission is limited, for example, the dashed line frame in fig. 2 shows the dimensions of the original bridge drive system eA1 in the X and Y directions (the outer envelope boundary dimensions including the motor and the reduction gears), and the dashed line frame shows the mounting dimensions of the vehicle interior space left for the bridge drive system in the X and Y directions. Obviously, under the limited installation size, the radial size of each gear can be reduced normally without changing the connection relationship of each component of the electric bridge drive system eA1, which can reduce the transmission ratio of the electric bridge drive system eA 1; at this time, in order to ensure the output torque, only the transmission torque of the motor can be increased, which results in an increase in system cost.
Therefore, how to reasonably arrange the bridge driving system in a limited space to enable the bridge driving system to have a larger transmission ratio is a problem to be solved in the field.
Disclosure of Invention
It is an object of the present invention to overcome or at least alleviate the above-mentioned deficiencies of the prior art and to provide a two speed drive system for an electric bridge.
The invention provides a two-speed bridge drive system having a radial and an axial direction and comprising a motor, a motor shaft, a double clutch, a plurality of gears, a planetary gear set and a differential, the motor shaft connecting a rotor of the motor and a driving part of the double clutch in a relatively non-rotatable manner, a first driven plate of the double clutch connecting one of the plurality of gears in a relatively non-rotatable manner, a second driven plate of the double clutch connecting another one of the plurality of gears in a relatively non-rotatable manner, the one gear being intended to transmit torque to a final gear of the plurality of gears via a first transmission path, the other gear being intended to transmit torque to the final gear via a second transmission path, wherein,
the sun gear of the planetary gear set is connected to the final gear in a rotationally fixed manner, and the planet carrier of the planetary gear set is connected to the housing of the differential in a rotationally fixed manner.
In at least one embodiment, the bridge driving system further comprises a first shaft and a second shaft, wherein the second shaft is a hollow shaft, the second shaft is sleeved on the first shaft and can rotate relative to the first shaft,
the first driven disk and the one gear are connected to the first shaft in a rotationally fixed manner, and the second driven disk and the other gear are connected to the second shaft in a rotationally fixed manner.
In at least one embodiment, the plurality of gears includes a first gear, a second gear, a third gear, a fourth gear, a fifth gear, and a sixth gear, the bridge drive system further includes an intermediate shaft,
said one gear being said first gear, said another gear being said second gear, said final gear being said sixth gear,
the third gear, the fourth gear and the fifth gear are connected with the intermediate shaft in a non-rotatable manner,
the first gear is meshed with the third gear, the second gear is meshed with the fourth gear, and the fifth gear is meshed with the sixth gear.
In at least one embodiment, the planetary gear set and the differential are located on a side of the sixth gear facing the electric machine in the axial direction.
In at least one embodiment, in the direction pointing from the electric motor to the dual clutch in the axial direction, the gears on the intermediate shaft are arranged in the following order: the fourth gear, the third gear, and the fifth gear.
In at least one embodiment, in the direction pointing from the electric motor to the dual clutch in the axial direction, the gears on the intermediate shaft are arranged in the following order: the fourth gear, the fifth gear, and the third gear.
In at least one embodiment, the first shaft and the intermediate shaft are disposed offset in the radial direction, and the output half shaft of the differential and the intermediate shaft are disposed offset in the radial direction.
In at least one embodiment, the sun gear and the final gear are mounted on an output axle shaft of the differential and are rotatable relative to the output axle shaft.
In at least one embodiment, the outer diameter of the ring gear of the planetary gear set is smaller than the outer diameter of the final gear.
In at least one embodiment, the plurality of gears are all spur gears.
The two-gear speed change electric bridge driving system has compact structure and can realize higher transmission ratio by using smaller size.
Drawings
FIG. 1 is a schematic diagram of a known two-speed electric bridge drive system.
Fig. 2 is a schematic view of the meshing relationship of the gears in fig. 1 as viewed in the axial direction.
Fig. 3 is a schematic diagram of a two-speed power bridge drive system according to a first embodiment of the present invention.
Fig. 4 is a schematic view of the meshing relationship of the gears in fig. 3 as viewed in the axial direction.
Fig. 5 is a schematic diagram of a two-speed power bridge drive system according to a second embodiment of the present invention.
Description of the reference numerals
E, a motor; a DC dual clutch; c1 first driven disk; c2 second driven disk; s1 first axis; s2 second axis; a Se motor shaft; sm intermediate shaft; s0 hollow shaft; g1 first gear; g2 second gear; g3 third gear; g4 fourth gear; g5 fifth gear; g6 sixth gear; a differential mechanism D; a PG planetary gear set; PG1 sun gear.
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. 3 and 5, unless otherwise specified, a denotes an axial direction of the bridge drive system, which axial direction a coincides with an axial direction of a shaft of the motor E in the bridge drive system; r denotes the radial direction of the bridge drive system, which corresponds to the radial direction of the shaft of the electric motor E in the bridge drive system.
(first embodiment)
Referring first to fig. 3 and 4, the structure of the bridge driving system eA2 according to the first embodiment of the present invention will be described.
The bridge drive system according to the present invention includes a motor E, a double clutch DC, a motor shaft Se, a first shaft S1, a second shaft S2, an intermediate shaft Sm, a plurality of gear pairs for speed change (three gear pairs in the present embodiment, a first gear G1 and a third gear G3 are engaged with each other to constitute one gear pair, a second gear G2 and a fourth gear G4 are engaged with each other to constitute one gear pair, and a fifth gear G5 and a sixth gear G6 are engaged with each other to constitute one gear pair), a planetary gear set PG, and a differential D.
The motor shaft Se connects the rotor of the electric motor E and the driving part of the double clutch DC in a rotationally fixed manner.
The first driven disk C1 of the dual clutch DC is connected in a rotationally fixed manner to the first shaft S1, and the second driven disk C2 of the dual clutch DC is connected in a rotationally fixed manner to the second shaft S2.
The second shaft S2 is a hollow shaft, and the second shaft S2 is sleeved on the first shaft S1, such that the first shaft S1 and the second shaft S2 can rotate relatively. The first shaft S1 is also non-rotatably connected with the first gear G1 and the second shaft S2 is also non-rotatably connected with the second gear G2.
The countershaft Sm is disposed offset in the radial direction R from the first shaft S1. The countershaft Sm is connected in a rotationally fixed manner to the third gear G3, the fourth gear G4 and the fifth gear G5. In the direction pointing to the double clutch DC from the motor E in the axial direction a, the gears on the countershaft Sm are arranged in the following order: a fourth gear G4, a third gear G3, and a fifth gear G5.
The output half shaft of the differential D is disposed offset in the radial direction R from the intermediate shaft Sm. Coaxially with the output axle shaft of the differential D, there are provided a planetary gear set PG and a sixth gear G6 (also called a final gear).
The sun gear PG1 of the planetary gear set PG is connected to the sixth gear G6 in a rotationally fixed manner, and the sun gear PG1 and the sixth gear G6 are both journalled on and rotatable relative to one output half shaft of the differential D. For example, sun gear PG1 and sixth gear G6 are connected in a rotationally fixed manner using a hollow shaft S0 journaled on one output half shaft of differential D, it being understood that hollow shaft S0, sun gear PG1 and sixth gear G6 may be formed as one body.
It should be understood that the differential D may also not include, but be connected to, output half shafts.
The planet carrier of the planetary gear set PG is connected in a rotationally fixed manner to the housing of the differential D, or the planet carrier can also be part of the housing of the differential D.
The ring gear of planetary gearset PG is fixedly connected, for example, to the housing of bridge drive eA2 in a rotationally fixed manner.
Preferably, the housings of the planetary gear set PG and the differential D are located at least partially between the electric machine E and the fifth gear G5 in the axial direction a, such an arrangement making reasonable use of the space between the electric machine E and the fifth gear G5 in the axial direction a, the distal end of the sixth gear G6 in the radial direction R (the portion farthest from the electric machine E in the sixth gear G6) and the electric machine E, so that the arrangement of the planetary gear set PG does not increase the size of the system in the axial direction a and the radial direction R.
Fig. 4 shows the gear mesh relationship of the bridge drive system eA2 according to the present invention viewed in the axial direction.
Preferably, the outer diameter of the ring gear of the planetary gear set PG is smaller than the outer diameter of the sixth gear G6. Thus, the arrangement of the planetary gear set PG does not increase the size of the system in the X and Z directions as shown in FIG. 4.
When the first driven plate C1 is engaged with the driving part of the dual clutch DC and the second driven plate C2 is disengaged from the driving part of the dual clutch DC, the bridge drive system eA2 is in the first speed gear. The power transmission path of the system at this time is as follows: a motor shaft Se, a driving part of the double clutch DC, a first driven disc C1, a first shaft S1, a first gear G1, a third gear G3, a middle shaft Sm, a fifth gear G5, a sixth gear G6, a hollow shaft S0, a sun gear PG1, a planet gear, a planet carrier and a differential D; wherein a first transmission path is constituted by the transmission paths of the first gear G1, the third gear G3, the counter shaft Sm, the fifth gear G5 to the sixth gear G6.
When the first driven disk C1 is disengaged from the driving part of the dual clutch DC and the second driven disk C2 is engaged with the driving part of the dual clutch DC, the bridge drive system eA2 is in the second speed gear. The power transmission path of the system at this time is as follows: a motor shaft Se, a driving part of the double clutch DC, a second driven disc C2, a second shaft S2, a second gear G2, a fourth gear G4, a middle shaft Sm, a fifth gear G5, a sixth gear G6, a hollow shaft S0, a sun gear PG1, a planet gear and a planet carrier-differential D; wherein the second transmission path is constituted by the transmission paths of the second gear G2, the fourth gear G4, the counter shaft Sm, the fifth gear G5 to the sixth gear G6.
Comparing bridge drive system eA2 with bridge drive system eA1, the provision of planetary gear set PG allows the gear ratio of the system to be increased without increasing the size of the system in the X and Z directions. On the other hand, each gear pair for speed change of the bridge drive system eA2 having the planetary gear set PG can have a smaller outer diameter for the same gear ratio, and especially when the outer diameters of the third gear G3, the fourth gear G4 and the sixth gear G6 are reduced, the bridge drive system eA2 can have a significantly reduced size in the X direction and the Z direction. For example, in the case of a gear ratio of 13 in the first speed gear, the size of the bridge drive system eA1 in the X and Y directions (including the outer envelope boundary size of the motor and each reduction gear) is shown by a dashed box in fig. 4, and the size of the bridge drive system eA2 in the X and Y directions is shown by a dashed box.
(second embodiment)
Referring next to fig. 5, a bridge drive system eA3 according to a second embodiment of the present invention will be described. The second embodiment is a modification of the first embodiment, and differs from the first embodiment mainly in the positions of the fifth gear G5, the sixth gear G6, the planetary gear set PG, and the differential D in the axial direction a.
In the direction pointing to the double clutch DC from the motor E in the axial direction a, the gears on the countershaft Sm are arranged in the following order: a fourth gear G4, a fifth gear G5, and a third gear G3.
The fifth gear G5 is located between the third gear G3 and the fourth gear G4 in the axial direction a, so that the sixth gear G6 meshing with the fifth gear G5, the planetary gear set PG connected to the sixth gear, and the differential D connected to the planetary gear set PG are all located closer to the electric motor E in the axial direction a, thereby more effectively utilizing the space close to the electric motor E in the axial direction a.
In the radial region where the sixth gear G6 is located, the bridge drive system eA3 frees more space at the axial end remote from the electric machine E than the bridge drive system eA2, while the bridge drive system eA2 frees more space at the axial end near the electric machine E than the bridge drive system eA 3.
The invention has at least one of the following advantages:
(i) the bridge drive system according to the present invention provides the planetary gear set PG between the speed change gear (sixth gear G6) and the differential D, and can appropriately reduce the gear ratio of the gear pair for speed change of the system, thereby reducing the diameter of each transmission gear pair, and reducing the size of the system in the X direction and the Z direction, while ensuring the gear ratio of the system.
(ii) The planetary gear set PG and the differential D of the bridge drive system according to the present invention are located on the side of the sixth gear G6 facing the electric machine E in the axial direction a, effectively utilizing the space which is located between the electric machine E and the fifth gear G5 in the axial direction a and which is not occupied by the first gear G1, the second gear G2, the third gear G3 and the fourth gear G4 in the radial direction R, so that the system structure is compact.
It should be understood that reference herein to the planetary gear set PG and the differential D being located on the side of the sixth gear G6 facing the electric machine E in the axial direction a means that all or most of the structure of the planetary gear set PG and the differential D is located on the side of the sixth gear G6 facing the electric machine E. As will be appreciated by those skilled in the art, the output half shaft (the right one in fig. 3 and 5) typically needs to pass out of the sixth gear G6 in order to transmit power to the wheels.
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. For example:
(i) preferably, the first gear G1, the second gear G2, the third gear G3, the fourth gear G4, the fifth gear G5 and the sixth gear G6 according to the present invention are all spur gears (including straight spur gears and helical spur gears), and preferably helical spur gears. The invention is not so limited.
(ii) The bridge drive system according to the invention can also have more gear pairs for speed reduction to increase the transmission ratio of the system, where space allows for example.
Claims (10)
1. A two-speed bridge drive system having a radial (R) and an axial direction (A) and comprising an electric motor (E), a motor shaft (Se), a Dual Clutch (DC), a plurality of gears, a planetary gear set (PG) and a differential (D), the motor shaft (Se) non-rotatably connecting a rotor of the electric motor (E) and a driving part of the Dual Clutch (DC), a first driven plate (C1) of the Dual Clutch (DC) non-rotatably connecting one of the plurality of gears, a second driven plate (C2) of the Dual Clutch (DC) non-rotatably connecting another of the plurality of gears for transmitting torque through a first transmission path to a final gear of the plurality of gears for transmitting torque through a second transmission path to the final gear, wherein the content of the first and second substances,
the sun gear (PG1) of the planetary gear set (PG) is connected to the final gear in a non-rotatable manner, and the planet carrier of the planetary gear set (PG) is connected to the housing of the differential (D) in a non-rotatable manner.
2. The two-speed shift bridge driving system according to claim 1, further comprising a first shaft (S1) and a second shaft (S2), wherein the second shaft (S2) is a hollow shaft, the second shaft (S2) is sleeved on the first shaft (S1) and can rotate relative to the first shaft (S1),
the first driven disk (C1) and the one gear are each connected to the first shaft (S1) so as not to be relatively rotatable, and the second driven disk (C2) and the other gear are each connected to the second shaft (S2) so as not to be relatively rotatable.
3. The two-speed power bridge driving system according to claim 2, wherein the plurality of gears includes a first gear (G1), a second gear (G2), a third gear (G3), a fourth gear (G4), a fifth gear (G5) and a sixth gear (G6), the power bridge driving system further includes a countershaft (Sm),
the one gear being the first gear (G1), the other gear being the second gear (G2), the final gear being the sixth gear (G6),
the third gear (G3), the fourth gear (G4) and the fifth gear (G5) are connected in a rotationally fixed manner to the countershaft (Sm),
the first gear (G1) is meshed with the third gear (G3), the second gear (G2) is meshed with the fourth gear (G4), and the fifth gear (G5) is meshed with the sixth gear (G6).
4. The two-speed bridge drive system according to claim 3, wherein in the axial direction (A) the planetary gear set (PG) and the differential (D) are located on the side of the sixth gear (G6) facing the electric machine (E).
5. The two-speed electrical bridge drive system according to claim 3 or 4, wherein the gears on the countershaft (Sm) are arranged in the sequence, in the axial direction (A) from the electric machine (E) towards the Double Clutch (DC): the fourth gear (G4), the third gear (G3), and the fifth gear (G5).
6. The two-speed electrical bridge drive system according to claim 3 or 4, wherein the gears on the countershaft (Sm) are arranged in the sequence, in the axial direction (A) from the electric machine (E) towards the Double Clutch (DC): the fourth gear (G4), the fifth gear (G5), and the third gear (G3).
7. The two-speed electrical bridge drive system according to claim 3 or 4, wherein the first shaft (S1) and the intermediate shaft (Sm) are arranged offset in the radial direction (R), and the output half shaft of the differential (D) and the intermediate shaft (Sm) are arranged offset in the radial direction (R).
8. The two-speed bridge drive system according to any of claims 1 to 4, wherein the sun gear (PG1) and the final gear are mounted on an output half shaft of the differential (D) and are rotatable relative to the output half shaft.
9. Two-speed gear shifting bridge drive system according to any of claims 1 to 4, wherein the outer diameter of the ring gear of the planetary gear set (PG) is smaller than the outer diameter of the final gear.
10. The two-speed variable bridge drive system according to any one of claims 1 to 4, wherein the plurality of gears are spur gears.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911259793.8A CN112937272A (en) | 2019-12-10 | 2019-12-10 | Two-gear speed change bridge driving system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911259793.8A CN112937272A (en) | 2019-12-10 | 2019-12-10 | Two-gear speed change bridge driving system |
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| Publication Number | Publication Date |
|---|---|
| CN112937272A true CN112937272A (en) | 2021-06-11 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911259793.8A Pending CN112937272A (en) | 2019-12-10 | 2019-12-10 | Two-gear speed change bridge driving system |
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| CN (1) | CN112937272A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102022204850A1 (en) | 2022-05-17 | 2023-11-23 | Zf Friedrichshafen Ag | Motor vehicle transmission, in particular axle transmission for a drive axle of an at least partially electrically driven motor vehicle |
-
2019
- 2019-12-10 CN CN201911259793.8A patent/CN112937272A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102022204850A1 (en) | 2022-05-17 | 2023-11-23 | Zf Friedrichshafen Ag | Motor vehicle transmission, in particular axle transmission for a drive axle of an at least partially electrically driven motor vehicle |
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