CN112238747A - Two keep off electric bridge actuating system and vehicle - Google Patents

Two keep off electric bridge actuating system and vehicle Download PDF

Info

Publication number
CN112238747A
CN112238747A CN201910656057.XA CN201910656057A CN112238747A CN 112238747 A CN112238747 A CN 112238747A CN 201910656057 A CN201910656057 A CN 201910656057A CN 112238747 A CN112238747 A CN 112238747A
Authority
CN
China
Prior art keywords
gear
clutch
transmission
planetary
housing
Prior art date
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
CN201910656057.XA
Other languages
Chinese (zh)
Inventor
刘磊
钟虎
翟青泉
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
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to CN201910656057.XA priority Critical patent/CN112238747A/en
Publication of CN112238747A publication Critical patent/CN112238747A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • 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
    • 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
    • B60K17/12—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of electric gearing

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Structure Of Transmissions (AREA)
  • Motor Power Transmission Devices (AREA)

Abstract

The invention provides a two-gear electric bridge driving system and a vehicle, wherein a transmission of the two-gear electric bridge driving system comprises a triple planetary gear mechanism and a first clutch and a second clutch which are independent of each other, the triple planetary gear mechanism only comprises a sun gear and three groups of planetary gears which are fixed with each other, the sun gear and one group of planetary gears are always in a meshing state, the other two groups of planetary gears are always in a meshing state with a gear ring respectively, and each gear ring is connected with a shell of the transmission through the first clutch and the second clutch. Thus, the two-speed bridge drive system according to the present invention is simpler in structure, lower in cost, small in axial size and weight, and easy to achieve good NVH control, as compared to the above-described two-speed drive bridge according to the prior art.

Description

Two keep off electric bridge actuating system and vehicle
Technical Field
The invention relates to the field of vehicles, in particular to a two-gear bridge driving system for a vehicle and the vehicle comprising the two-gear bridge driving system.
Background
Currently, bridge drive systems can be used for electric-only vehicles and hybrid vehicles for the driving of the vehicle.
Fig. 1 is a schematic diagram showing a connection structure of a two-speed bridge driving system according to the related art. As shown in fig. 1, the two-speed bridge drive system comprises an electric machine EM, a transmission, a differential DM and two half-shafts HS1, HS2, which are integrated together.
Specifically, the motor EM has a hollow output shaft S1.
Further, the transmission is a dual clutch transmission comprising a housing and disposed therein a hollow first input shaft S21, a hollow second input shaft S22, a planetary gear mechanism and a dual clutch having two clutch units K11, K12.
The first input shaft S21 and the second input shaft S22 are connected coaxially with the output shaft S1 via a dual clutch, so that the first input shaft S21 can be drivingly coupled to the output shaft S1 by engagement of the first clutch unit K11, and the second input shaft S22 can be drivingly coupled to the output shaft S1 by engagement of the second clutch unit K12. The second input shaft S22 passes through the first input shaft S21 and is located radially inward of the first input shaft S21, and the second input shaft S22 is rotatable independently of the first input shaft S21.
The planetary gear mechanism includes a first sun gear SU1, a second sun gear SU2, a plurality of first planet gears PG1, a plurality of second planet gears PG2, a plurality of third planet gears PG3, a first ring gear R1, and a carrier P. The first sun gear SU1 is fixed to the first input shaft S21 and is always in mesh with the plurality of third planetary gears PG3, and the second sun gear SU2 is fixed to the second input shaft S22 and is always in mesh with the plurality of second planetary gears PG 2. One first planetary PG1, one second planetary PG2, and one third planetary PG3 are in a group and fixed to each other. The carrier P serves to hold a plurality of first planetary gears PG1, a plurality of second planetary gears PG2, and a plurality of third planetary gears PG3 at the same time, and is drivingly coupled with the housing of the differential DM. The first ring gear R1 is always in mesh with the plurality of first planetary gears PG1 and the first ring gear R1 is fixed relative to the case of the transmission.
The dual clutch is a wet clutch and includes the first clutch unit K11 and the second clutch unit K12 that can be operated independently of each other as described above.
Further, a miniaturized differential DM having a relatively complicated structure is integrated into a housing of the transmission. Two half shafts HS1, HS2 extend from differential DM towards both sides, with a first half shaft HS1 extending through second input shaft S22, the dual clutch and output shaft S1, and a second half shaft HS2 extending out of the transmission housing in a direction opposite to the direction of extension of first half shaft HS 1.
Thus, when the first clutch unit K11 is engaged, the transmission path of torque from the electric machine EM is as follows: electric machine EM → output shaft S1 → first input shaft S21 → first sun gear SU1 → third planet PG3 → first planet PG1 → carrier P → differential DM. When the second clutch K2 is engaged, the transmission path of torque from the electric machine EM is as follows: electric machine EM → output shaft S1 → second input shaft S22 → second sun gear SU2 → second planet gears PG2 → first planet gears PG1 → carrier P → differential DM.
Further, the transmission housing includes a first housing portion H11, a second housing portion H12, and a third housing portion H13 that are removably secured to one another. The dual clutches are located within the third housing portion H13 and the other components of the transmission and the differential DM are located within the mounting space enclosed by the first housing portion H11 and the second housing portion H12. In addition, the housing also includes a partition disposed between the second housing segment H12 and the third housing segment H13.
Although the bridge drive system shown in fig. 1 is capable of two-gear drive, it has the following disadvantages:
i. since the two-speed bridge drive system has the double clutch and the corresponding bearing support structure and the differential with a more complicated structure for miniaturization, the cost of the whole system is high, and moreover, the surface needing to be sealed is excessive due to the fact that the partition part of the shell of the transmission is supported by the bearing, so that the cost is high;
since the two-speed bridge drive system has a plurality of hollow shafts (the first input shaft S21 and the second input shaft S22) which are coaxial with one another, the accuracy requirement and the cost are high, and the hollow shafts result in that the diameters of the sun gears SU1, SU2 mounted thereon cannot be sufficiently small, which imposes undesirable restrictions on the transmission ratio of the transmission; and
the two sun gears SU1, SU2 and the corresponding portions of the two input shafts S21, S22 protruding from the bearings and the dual clutch form a cantilever structure, thus resulting in poor and unstable support rigidity of the two sun gears SU1, SU2, and thus poor NVH control is difficult to achieve.
Disclosure of Invention
The present invention has been made in view of the above-mentioned drawbacks of the prior art. It is an object of the present invention to provide a novel two-speed bridge drive system which is simpler in construction, less costly, has a small axial size and weight, and is susceptible to good NVH control, as compared to the two-speed bridge drive systems according to the prior art described above. Another object of the present invention is to provide a vehicle including the two-speed bridge drive system described above.
In order to achieve the above object, the present invention adopts the following technical solutions.
The invention provides a two-gear bridge driving system, which comprises:
a motor having an output shaft; and
a transmission including an input shaft for driving coupling with the output shaft, a triple planetary gear mechanism, a first clutch and a second clutch,
the triple planetary gear mechanism comprises a sun gear, a plurality of first planetary gears, a plurality of second planetary gears, a plurality of third planetary gears, a planetary carrier, a first gear ring and a second gear ring, wherein the sun gear is fixed on the input shaft and is always engaged with the third planetary gears, the first planetary gears are fixed with the third planetary gears, the first gear ring is always engaged with the first planetary gears, the second gear ring is always engaged with the second planetary gears, the planetary carrier is used for transmitting torque to the outside, and the third planetary gears are fixed with the first planetary gears
The first clutch engagement enables the first ring gear to be relatively fixed with respect to a housing of the transmission, and the first clutch disengagement allows the first ring gear to be rotatable with respect to the housing of the transmission, the second clutch engagement enables the second ring gear to be relatively fixed with respect to the housing of the transmission, and the second clutch disengagement allows the second ring gear to be rotatable with respect to the housing of the transmission.
Preferably, the input shaft of the transmission is directly connected to the output shaft of the motor in a coaxial manner, and the third planetary gear is closer to the motor than the first planetary gear and the second planetary gear.
More preferably, the two-speed bridge drive system further comprises a differential and two half shafts extending from the differential, the planet carrier being drivingly coupled to the differential input gear of the differential.
More preferably, the output shaft and the input shaft are both hollow shafts, the two half shafts are arranged coaxially with the output shaft and the input shaft, and one of the two half shafts extends through the output shaft and the input shaft.
More preferably, the differential is a bevel gear differential, and the planetary carrier is fixedly connected with a housing of the bevel gear differential.
More preferably, when the first clutch (K1) is engaged, the transmission is capable of achieving a first gear ratio as follows: (1+ Z)R1/ZSU)×(ZPG3/ZPG1) Wherein Z isR1Is the number of teeth, Z, of the first ring gear (R1)SUIs the number of teeth of the sun gear (SU), ZPG1Is the number of teeth, Z, of the first planet wheel (PG1)PG3Is the number of teeth of the third planet wheel (PG 3).
More preferably, when the second clutch (K2) is engaged, the transmission is capable of achieving a second gear ratio as follows: (1+ Z)R2/ZSU)×(ZPG3/ZPG2) Wherein Z isR2Is the number of teeth, Z, of the second ring gear (R2)SUIs the sun gear(SU) number of teeth, ZPG2Is the number of teeth, Z, of said second planet wheel (PG2)PG3Is the number of teeth of the third planet wheel (PG 3).
More preferably, the housing of the transmission comprises a first housing part and a second housing part connected to each other in the axial direction, a part of the second housing part also serving to constitute a housing of the electric machine.
More preferably, the first clutch and the second clutch are both wet multiplate clutches.
The invention further provides a vehicle comprising the two-gear bridge driving system in any one of the above technical solutions.
By adopting the technical scheme, the invention provides a novel two-gear electric bridge driving system and a vehicle comprising the same, wherein a transmission of the two-gear electric bridge driving system comprises a triple planetary gear mechanism, a first clutch and a second clutch which are independent of each other, the triple planetary gear mechanism only comprises a sun gear and three groups of planetary gears which are fixed with each other, the sun gear and one group of planetary gears are always in a meshing state, the other two groups of planetary gears are always in a meshing state with a gear ring, and each gear ring is connected with a shell of the transmission through the first clutch and the second clutch. Thus, the two-speed bridge drive system according to the present invention is simpler in structure, lower in cost, small in axial size and weight, and easy to achieve good NVH control, as compared to the above-described two-speed drive bridge according to the prior art.
Drawings
Fig. 1 is a schematic diagram showing a connection structure of a two-speed bridge driving system according to the related art.
Fig. 2 is a schematic diagram showing a connection structure of a two-speed bridge driving system according to an embodiment of the present invention.
Description of the reference numerals
EM motor S1 output shaft
S2 input shaft S21 first input shaft S22 second input shaft SU sun gear SU1 first sun gear SU2 second sun gear PG1 first planet gear PG2 second planet gear PG3 third planet gear P planet gear carrier R1 first ring gear R2 second ring gear K1 first clutch K2 second clutch K11 first clutch unit K12 second clutch unit K12
H11 first housing part H12 second housing part H13 third housing part H21 first housing part H22 second housing part
The DM differential HS1 has a first half shaft HS2 and a second half shaft.
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.
In the present invention, "transmission coupling" means that two members are connected to be able to transmit driving force/torque, and, as there is no particular description, it may mean that the two members are directly connected or coupled via a related art transmission structure such as a gear mechanism to be able to transmit driving force/torque between the two members. In the present invention, "axial direction" refers to the axial direction of the output shaft of the motor and the input shaft of the transmission, "one axial direction side" refers to the right side in fig. 2, and "the other axial direction side" refers to the left side in fig. 2.
As shown in fig. 2, the two-speed bridge drive system according to an embodiment of the invention comprises an electric machine EM, a transmission, a differential DM and two half-shafts HS1, HS2, which are in driving connection.
Specifically, in the present embodiment, the motor EM has a hollow output shaft S1 for outputting torque. Two bearings for supporting the output shaft S1 are disposed in the axial direction, and the two bearings support both axial end portions of the output shaft S1.
In the present embodiment, the transmission is located entirely on one axial side of the electric machine EM and includes a hollow input shaft S2, a triple planetary gear mechanism, and two clutches K1, K2.
The input shaft S2 of the transmission is directly connected coaxially with the output shaft S1 of the electric machine EM, so that the transmission can receive torque from the electric machine EM. The above "directly connected in a coaxial manner" means that the input shaft S2 of the transmission and the output shaft S1 of the electric machine EM may be the same shaft or that the input shaft S2 of the transmission and the output shaft S1 of the electric machine EM are rigidly connected in a coaxial manner, and the same expressions in this application have the same meaning.
The triple planetary gear mechanism includes one sun gear SU, a plurality of first planet gears PG1, a plurality of second planet gears PG2, a plurality of third planet gears PG3, a first ring gear R1, a second ring gear R2, and a carrier P. The sun gear SU is fixed to the input shaft S2 of the transmission and is constantly in mesh with the plurality of third planetary gears PG3, and the third planetary gear PG3 is located on the motor side, i.e., on the other axial side, than the first planetary gear PG1 and the second planetary gear PG 2. In the present invention, when "gear" is fixed to "shaft", it is generally meant that the gear and shaft can rotate together, but the gear and shaft are not allowed to be completely fixed in the axial direction of the shaft. The plurality of first planets PG1, the plurality of second planets PG2, and the plurality of third planets PG3 share the carrier P. Each of the first planet gears PG1 is grouped with a corresponding one of the second planet gears PG2 and a corresponding one of the third planet gears PG3 to be fixedly connected to constitute a triple gear. In fact, it is not necessary to rigidly connect the first planet PG1 and the corresponding second and third planet PG2 and PG3, as long as each first planet PG1 can rotate together with the corresponding second and third planet PG2 and PG 3. The first ring gear R1 and the plurality of first planet gears PG1 are always in a meshed state, and the second ring gear R2 and the plurality of second planet gears PG2 are always in a meshed state. The planetary carrier P is used to transmit torque to the differential DM.
Further, the first ring gear R1 is connected to the first housing portion H21 of the housing of the transmission via the first clutch K1, so that the first ring gear R1 can be fixed relative to the housing of the transmission by engagement of the first clutch K1. The second ring gear R2 is connected to the second housing part H22 of the transmission housing via the second clutch K2, so that the second ring gear R2 can be fixed relative to the transmission housing by engagement of the second clutch K2. In the present embodiment, the first clutch K1 and the second clutch K2 are both wet multiplate clutches that can be operated independently.
Further, in the present embodiment, the differential DM is a conventional bevel gear differential DM. The shell of the bevel gear differential is fixedly connected with a planet gear carrier P of the triple planetary gear mechanism. Four bevel gears are arranged inside the housing, which are engaged with each other, wherein two bevel gears facing each other are mounted on and rotatable about a planetary shaft fixed to the housing, and the other two bevel gears are fixedly connected to two half shafts HS1, HS2, respectively. Although the differential DM is integrated into the transmission in the present embodiment, the differential DM may alternatively be made independent of the transmission. Further, in the present embodiment, two half shafts HS1, HS2 extend from the differential DM toward both axial sides, wherein a first half shaft HS1 extends from the differential DM toward the other axial side through the hollow input shaft S2 of the transmission and the hollow output shaft S1 of the electric machine EM in sequence, the first half shaft HS1 is rotatable independently of the input shaft S2, and a second half shaft HS2 extends from the differential DM toward one axial side out of the first housing portion H21 of the housing of the transmission. In this way, torque from the electric machine EM can be transmitted via the transmission to the differential DM and thus to the half-shafts HS1, HS2 and the wheels of the vehicle.
Thus, in the present embodiment, when the first clutch K1 is engaged, the transmission path of the torque from the electric machine EM is as follows: electric machine EM → output shaft S1 → input shaft S2 → sun gear SU → third planet PG3 → first planet PG1 → carrier P → differential DM; and the transmission is now able to achieve the following first gear ratio: (1+ Z)R1/ZSU)×(ZPG3/ZPG1) Wherein Z isR1Is the number of teeth, Z, of the first ring gear R1SUIs the number of teeth of the sun gear SU, ZPG1Is the number of teeth of the first planet gear PG1, ZPG3Is the number of teeth of the third planet PG 3.
In the present embodiment, when the second clutch K2 is engaged, the transmission path of the torque from the electric machine EM is as follows: electric machine EM → output shaft S1 → input shaft S2 → sun gear SU → third planet gear PG3 → second planet gear PG2 → carrier P → differential DM; and the transmission can now realize the second transmissionThe ratio is as follows: (1+ Z)R2/ZSU)×(ZPG3/ZPG2) Wherein Z isR2Is the number of teeth of the second ring gear R2, ZSUIs the number of teeth of the sun gear SU, ZPG2Is the number of teeth, Z, of the second planet gear PG2PG3Is the number of teeth of the third planet PG 3.
In the normal operating state, only one of the first clutch K1 and the second clutch K2 is engaged, and not simultaneously.
In addition, since the structure inside the transmission is simplified, the housing of the transmission may include only the first housing portion H21 and the second housing portion H22 detachably connected to each other. The other components of the transmission are housed and mounted in a mounting space surrounded by the first case portion H21 and the second case portion H22. A part of the second housing part H22 also serves to constitute the housing of the electric machine.
In addition, the invention also provides a vehicle comprising the two-gear electric bridge driving system.
Although the technical solutions of the present invention have been described in detail in the above embodiments, the following descriptions are also required.
i. Although not specifically described in the above embodiments, it should be understood that in each of the above embodiments, the electric motor EM can receive torque from the transmission for charging the battery, in addition to outputting torque to the transmission for driving.
Although not specifically described in the above embodiments, it is to be understood that the output shaft S1 of the motor, the input shaft S2 of the transmission, and the carrier P are all supported by corresponding bearings.
Since the two-gear drive system according to the invention omits the double clutch and simplifies the planetary gear mechanism with respect to the two-gear drive system according to the prior art described above, the disadvantages described in the background are avoided.
Since the two clutches K1, K2 in the two-speed drive system according to the invention use the space radially outside (the triple gear and the ring gear) in the transmission, the overall transmission and the two-speed drive system have smaller axial dimensions and are more compact; and because the clutches K1, K2 in the two-gear driving system are independent modular components, the two-gear driving system has simple structure, low cost and easy control compared with a double clutch; since the support structure of the input shaft S2 and sun gear SU of the transmission in the two-speed drive system according to the present invention is simple and reliable, the reliability of the system and NVH control are improved; the two-gear driving system uses the traditional differential mechanism, so that the cost is saved; since there is no structure in the two-gear drive system according to the invention like a hollow shaft surrounding a hollow shaft in the two-gear drive system according to the prior art, costs are saved.
v. although not explicitly stated in the above specific embodiments, preferably, ZPG3>ZPG1>ZPG2>ZSUAnd ZR1>ZSU，ZR2>ZSU(ii) a In addition, in each embodiment, when the gear ratio is calculated in accordance with the above formulas, the modules of the gears may be the same.

Claims (10)

1. A two-speed bridge drive system, comprising:
an Electric Machine (EM) having an output shaft (S1); and
a transmission including an input shaft (S2) for driving coupling with the output shaft (S1), a triple planetary gear mechanism, a first clutch (K1) and a second clutch (K2),
the triple planetary gear mechanism comprises a sun gear (SU), a plurality of first planetary gears (PG1), a plurality of second planetary gears (PG2), a plurality of third planetary gears (PG3), a planetary carrier (P) and a first gear ring (R1) and a second gear ring (R2), wherein the sun gear (SU) is fixed on an input shaft (S2) and is always engaged with the plurality of third planetary gears (PG3), the first planetary gear (PG1), the second planetary gear (PG2) and the third planetary gear (PG3) are fixed with each other, the first gear ring (R1) and the first planetary gear (PG1) are always engaged with each other, the second gear ring (R2) and the second planetary gear (PG2) are always engaged with each other, the planetary carrier (P) is used for transferring torque to the outside, and the planetary carrier (P) is used for transferring torque to the outside
The first clutch (K1) is engaged to enable the first ring gear (R1) to be relatively fixed with respect to a housing of the transmission, and the first clutch (K1) is disengaged to allow the first ring gear (R1) to be rotatable with respect to the housing of the transmission, the second clutch (K2) is engaged to enable the second ring gear (R2) to be relatively fixed with respect to the housing of the transmission, and the second clutch (K2) is disengaged to allow the second ring gear (R2) to be rotatable with respect to the housing of the transmission.
2. The two-speed bridge drive system according to claim 1, wherein the input shaft (S2) of the transmission is directly connected to the output shaft (S1) of the Electric Machine (EM) in a coaxial manner, and the third planetary gear (PG3) is located on the side of the Electric Machine (EM) with respect to the first planetary gear (PG1) and the second planetary gear (PG 2).
3. The two-gear bridge drive system according to claim 2, further comprising a Differential (DM) and two half-shafts (HS1, HS2) extending from the Differential (DM), the planet wheel carrier (P) being drivingly coupled with a differential input gear of the Differential (DM).
4. The two-speed bridge drive system according to claim 3,
the output shaft (S1) and the input shaft (S2) are both hollow shafts,
the two half shafts (HS1, HS2) are arranged coaxially with the output shaft (S1) and the input shaft (S2), and one half shaft (HS1) of the two half shafts (HS1, HS2) extends through the output shaft (S1) and the input shaft (S2).
5. The two-speed bridge drive system according to claim 3 or 4, wherein the Differential (DM) is a bevel gear differential, the planet wheel carrier (P) being fixedly connected to a housing of the bevel gear differential.
6. The two-speed bridge drive system according to any one of claims 1 to 4,
when the first clutch (K1) is engaged, the transmission is capable of achieving a first gear ratio as follows: (1+ Z)R1/ZSU)×(ZPG3/ZPG1) Wherein Z isR1Is the number of teeth, Z, of the first ring gear (R1)SUIs the number of teeth of the sun gear (SU), ZPG1Is the number of teeth, Z, of the first planet wheel (PG1)PG3Is the number of teeth of the third planet wheel (PG 3).
7. The two-speed bridge drive system according to any one of claims 1 to 4,
when the second clutch (K2) is engaged, the transmission is capable of achieving a second gear ratio as follows: (1+ Z)R2/ZSU)×(ZPG3/ZPG2) Wherein Z isR2Is the number of teeth, Z, of the second ring gear (R2)SUIs the number of teeth of the sun gear (SU), ZPG2Is the number of teeth, Z, of said second planet wheel (PG2)PG3Is the number of teeth of the third planet wheel (PG 3).
8. The two-speed bridge drive system according to any one of claims 1 to 4, wherein the transmission housing comprises a first housing part (H21) and a second housing part (H22) which are connected to each other in the axial direction, a part of the second housing part (H22) also serving to constitute a housing for the Electric Machine (EM).
9. The two-speed bridge drive system according to any one of claims 1 to 4, wherein the first clutch (K1) and the second clutch (K2) are both wet multiplate clutches.
10. A vehicle comprising a two-speed bridge drive system according to any one of claims 1 to 9.
CN201910656057.XA 2019-07-19 2019-07-19 Two keep off electric bridge actuating system and vehicle Pending CN112238747A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201910656057.XA CN112238747A (en) 2019-07-19 2019-07-19 Two keep off electric bridge actuating system and vehicle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201910656057.XA CN112238747A (en) 2019-07-19 2019-07-19 Two keep off electric bridge actuating system and vehicle

Publications (1)

Publication Number Publication Date
CN112238747A true CN112238747A (en) 2021-01-19

Family

ID=74167694

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201910656057.XA Pending CN112238747A (en) 2019-07-19 2019-07-19 Two keep off electric bridge actuating system and vehicle

Country Status (1)

Country Link
CN (1) CN112238747A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023137661A1 (en) * 2022-01-20 2023-07-27 舍弗勒技术股份两合公司 Electric axle drive system and vehicle

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023137661A1 (en) * 2022-01-20 2023-07-27 舍弗勒技术股份两合公司 Electric axle drive system and vehicle

Similar Documents

Publication Publication Date Title
CN112238746A (en) Two keep off electric bridge actuating system and vehicle
US10808814B2 (en) Transaxle and two-speed drive module thereof
JP2007050877A (en) Power system for hybrid vehicle
US10495191B1 (en) Transmission of motor driving vehicle
CN112776598A (en) Two-gear speed change bridge driving system
CN112238747A (en) Two keep off electric bridge actuating system and vehicle
US11370299B2 (en) Power transmission device
CN111828565A (en) Speed change mechanism and bridge drive system
CN116373596A (en) High-efficiency four-gear electric drive bridge transmission system
CN112549954A (en) Two keep off electric bridge actuating system and vehicle
CN114222677A (en) Two-gear speed change bridge driving system with double clutches
CN112721619A (en) Two-gear speed change bridge driving system without power interruption
WO2023173318A1 (en) Bridge driving system and vehicle
CN215552500U (en) Dual-motor power system and automobile
US20210252959A1 (en) Electric solid axle
CN114435106A (en) Electric drive axle structure for hybrid new energy automobile
CN112937272A (en) Two-gear speed change bridge driving system
CN114103614A (en) Two-gear speed change bridge driving system
CN112693307A (en) Two keep off electric bridge actuating system and vehicle
CN112776597A (en) Two-gear speed change bridge driving system
CN210770068U (en) Power transmission mechanism
CN217381535U (en) Gearbox, driving system and vehicle
CN219198016U (en) Power transmission device, power assembly and vehicle
CN110901358A (en) Electric bridge driving system and vehicle
CN219487173U (en) Power drive system

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination