CN115742733A - Two grades of formula electric transaxles and new energy automobile - Google Patents
Two grades of formula electric transaxles and new energy automobile Download PDFInfo
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- CN115742733A CN115742733A CN202211482242.XA CN202211482242A CN115742733A CN 115742733 A CN115742733 A CN 115742733A CN 202211482242 A CN202211482242 A CN 202211482242A CN 115742733 A CN115742733 A CN 115742733A
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Abstract
The invention discloses a two-gear electric drive axle and a new energy automobile, and relates to the field of automobiles, wherein the two-gear electric drive axle comprises a motor and a speed change differential mechanism, wherein a long half shaft penetrates through the motor; the variable speed differential mechanism is detachably connected to one end of the motor and comprises an electromagnetic clutch, an NGW type planetary row and a double-inner meshing planetary row which are sequentially arranged along a long half shaft, an electromagnetic brake is arranged between the NGW type planetary row and the variable speed differential shell, and one end of the long half shaft is connected with a short half shaft through a differential mechanism; different gears are switched by switching on and off the electromagnetic brake and the electromagnetic clutch. The invention realizes the output of two speed reduction ratios by the matching of the clutch and the brake, has larger speed regulation range compared with the traditional single planet row, and can meet the rotating speed output of vehicles under different working conditions; compact structure is favorable to improving the trafficability characteristic of the automobile and saving the installation space.
Description
Technical Field
The invention relates to the field of automobiles, in particular to a two-gear electric drive axle and a new energy automobile.
Background
The drive axle is an electromechanical integration product formed by combining a speed reducer, an inverter and a motor, and occupies an important position in the fields of new energy electric automobiles and the like. The arrangement form of the existing two-gear transmission of the electric vehicle mostly adopts a parallel shaft type and a planet row type, the two-gear transmission adopting the parallel shaft type arrangement form realizes the switching of gears through a synchronizer or a clutch, and if the switching of the gears is realized by adopting the synchronizer and the like, the two-gear transmission has the following defects: the gear shifting actuating mechanism needs to be independently installed, so that the volume of a driving system is increased, the whole vehicle is inconvenient to arrange, and the power interruption exists in the gear shifting process.
For a two-speed transmission with a planetary arrangement, the gears are usually shifted by means of a clutch or brake combination, but the following disadvantages are encountered: the gear shift actuators are relatively discrete and the transmission and differential are large in size, resulting in a drive system that is not compact enough and the rotational speeds of the output power cannot be matched.
Disclosure of Invention
Aiming at the defects in the prior art, the invention aims to provide a two-gear electric drive axle and a new energy automobile, which realize the output of two reduction ratios by matching a clutch and a brake, have larger speed regulation range compared with the traditional single planet row and can meet the rotating speed output of the automobile under different working conditions; compact structure is favorable to improving the trafficability characteristic of the automobile and saving the installation space.
In order to realize the purpose, the invention is realized by the following technical scheme:
in a first aspect, an embodiment of the present invention provides a two-gear electric transaxle, including:
the motor is internally provided with a long half shaft which penetrates through;
the variable speed differential mechanism is detachably connected to one end of the motor and comprises an electromagnetic clutch, an NGW type planetary row and a double-inner meshing planetary row which are sequentially arranged along a long half shaft, an electromagnetic brake is arranged between the NGW type planetary row and the variable speed differential shell, and one end of the long half shaft is connected with a short half shaft through a differential mechanism; different gears are switched by switching on and off the electromagnetic brake and the electromagnetic clutch.
As a further implementation manner, the NGW type planet row comprises an NGW type inner gear ring, an NGW type planet wheel, an NGW type sun gear and an NGW type planet carrier, wherein the NGW type sun gear is fixed with the long half shaft;
the NGW type annular gear is connected with the speed-changing differential shell through an electromagnetic brake; and the NGW type planet gear is connected with an NGW type planet carrier, and the NGW type planet carrier is fixedly connected with the input end eccentric mechanism.
As a further implementation mode, the input end of the electromagnetic clutch is connected with the motor rotor, and the output end of the electromagnetic clutch is connected with the NGW type planet carrier.
As a further implementation manner, the double internal meshing planetary row comprises a double internal meshing inner gear ring, a double internal meshing conjugate gear ring and a double internal meshing sun gear, the double internal meshing sun gear is mounted on the long half shaft through a bearing, and the double internal meshing conjugate gear ring is respectively meshed with the double internal meshing inner gear ring and the double internal meshing sun gear.
As a further implementation, the double inner-meshing sun gear is fixedly connected with the differential frame, and the double inner-meshing ring gear is fixedly connected with the speed change differential shell.
As a further implementation mode, one end of the double inner-meshing conjugate gear ring is connected with one end of the output end eccentric mechanism through a bearing, and the other end of the output end eccentric mechanism is matched with the speed change differential end cover through a bearing; the speed change differential end cover is arranged at the end part of the speed change differential shell.
As a further implementation mode, an output end axle housing is installed on the outer side of the short half shaft, and the output end axle housing is detachably connected with the variable speed differential housing; and a motor end axle housing is arranged on the outer side of the long half shaft and is detachably connected with the motor shell.
As a further implementation mode, one end of the short half shaft extending out of the output end axle housing and one end of the long half shaft extending out of the motor end axle housing are respectively connected with the flange plates.
In a second aspect, the embodiment of the invention further provides a new energy automobile, which includes the two-gear electric drive axle.
As a further implementation manner, the axle housing of the two-gear electric drive axle is connected with the vehicle body through a damping device; and the long half shaft and the short half shaft are respectively connected with the wheel hub through flange plates.
The invention has the following beneficial effects:
(1) The invention adopts the mode of coaxial arrangement of the double inner meshing planetary rows and the NGW type planetary rows, so that the structure of the speed reducing motor is more compact, and the improvement of the automobile trafficability and the saving of the installation space are facilitated; the output of two speed reduction ratios is realized through the matching of the clutch, the rack and the brake, and compared with the traditional single planet row, the speed regulation range is wider, and the rotating speed output of the vehicle under different working conditions can be met; the coaxial structure of the high-speed NGW planetary gear train and the low-speed inner meshing planetary gear train in series is adopted, so that the reduction ratio is considerable on the premise of compact structure.
(2) The double internal meshing planetary gear train adopts the gear with large contact ratio, can ensure that the electric bridge meets the requirement of gear meshing strength and further reduces the size when outputting low-speed and large torque, has small tooth surface impact when meshing the gears, and prolongs the service life.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate exemplary embodiments of the invention and together with the description serve to explain the invention and not to limit the invention.
FIG. 1 is a schematic illustration of a two-speed electric drive axle configuration according to one or more embodiments of the present disclosure;
FIG. 2 is a schematic illustration of the reduction mechanism assembled with a differential mechanism in accordance with one or more embodiments of the present invention;
FIG. 3 is a schematic diagram of an internal structure of a two-speed electric transaxle according to one or more embodiments of the present invention;
FIG. 4 is a schematic illustration of a two-speed electric drive axle configuration according to one or more embodiments of the present disclosure;
FIG. 5 is a schematic illustration of an eccentric mechanism attachment according to one or more embodiments of the present disclosure;
FIG. 6 is a schematic illustration of a two-speed electric transaxle high speed gear of the present invention in accordance with one or more embodiments;
FIG. 7 is a schematic low gear of a two-speed electric transaxle according to one or more embodiments of the present invention.
The system comprises a speed change differential mechanism 1, a speed change differential mechanism 11, a speed change differential shell 12, a speed change differential end cover 13, a double inner meshing planetary row 131, a double inner meshing inner gear ring 132, a double inner meshing conjugate gear ring 133, a double inner meshing sun gear 134, an output end eccentric mechanism 135 and an input end eccentric mechanism; 14. differential, 141, a differential frame, 142, a differential bevel gear, 143, a fixed nut, 15, an NGW type planet row, 151, an NGW type annular gear, 152, an NGW type planet gear, 153, an NGW type sun gear, 154, an NGW type planet carrier, 16, an electromagnetic brake, 17, an electromagnetic clutch, 171, an electromagnetic clutch input end, 172 and an electromagnetic clutch output end; 2. outer end interface 3, motor 31, motor housing 32, motor stator 33, motor rotor 4, output half shaft 41, short half shaft 42, long half shaft 5, axle housing 51, output end axle housing 52 and motor end axle housing.
Detailed Description
The first embodiment is as follows:
the embodiment provides a two-gear electric drive axle, as shown in fig. 1, which includes a speed change differential mechanism 1, a motor 3, an output axle shaft 4 and an axle housing 5, which are coaxially arranged, wherein the speed change differential mechanism 1 is connected to one end of the motor 3, the motor 3 and the speed change differential mechanism 1 are respectively and correspondingly connected to the output axle shaft 4, and the axle housing 5 is respectively mounted on the outer side of the output axle shaft 4; reasonable arrangement and compact structure.
As shown in fig. 3, the electric motor 3 includes a motor housing 31, a motor stator 32, and a motor rotor 33, the motor stator 32 and the motor rotor 33 are installed in the motor housing 31, and the long axle shaft 42 penetrates through the motor rotor 33, wherein one end of the long axle shaft 42 is connected to the differential speed change mechanism 1, the other end is connected to and extends out of the motor housing 31, a motor end axle housing 52 is arranged outside the end, and the motor end axle housing 52 is detachably connected to the motor housing 31. The motor housing 31 is provided with an outer end interface 2.
As shown in fig. 2, the speed change differential mechanism 1 adopts two-gear speed change for changing the speed of the output power of the motor 3, i.e. realizing high-gear and low-gear speed change; the speed-changing differential mechanism 1 comprises a double inner meshing planetary row 13, a differential 14, an NGW type planetary row 15, an electromagnetic brake 16 and an electromagnetic clutch 17, wherein the NGW type planetary row 15 is in array but has poor bearing capacity, so that the speed-changing differential mechanism is used for high-speed reduction; the double inner meshing planetary row 13 has a strong bearing capacity because the conjugate gear ring is in inner meshing with the sun gear and the inner gear ring, but has a complex structure and is easy to generate eccentric vibration because of an eccentric mechanism.
The electromagnetic clutch 17, the NGW type planetary row 15, the double inner meshing planetary row 13 and the differential 14 are sequentially arranged from the end close to the motor to the other end, and an electromagnetic brake 16 is arranged on the outer side of the NGW type planetary row 15; the electromagnetic clutch 17, the NGW type planetary row 15 and the double inner meshing planetary row 13 are all arranged on an output half shaft 4 of the corresponding motor, namely a long half shaft 42; differential 14 is connected at one end to long half shaft 42 and at the other end to short half shaft 41, i.e., to output half shaft 4 of variable speed differential mechanism 1.
As shown in fig. 3, the electromagnetic clutch 17, the NGW type planetary row 15 and the double inter-meshing planetary row 13 are mounted in a speed change differential housing 11, one end of the speed change differential housing 11 is detachably connected with the motor 3, and the other end is mounted with a speed change differential end cover 12; the speed change differential cover 12 is connected to the output-side axle housing 51, and the stub axle 41 penetrates the output-side axle housing 51.
In the present embodiment, the major axis 42 and the minor axis 41 are relative concepts, and the length of the major axis 42 is greater than the length of the minor axis 41.
In order to further improve the bearing capacity of the electric drive axle and improve the transmission stability, the double inner meshing planetary row 13 of the embodiment adopts a tooth form with a large contact ratio, so that the torque load is uniformly distributed on more tooth pairs. In order to make the axial dimension of the two-stage speed reducer as small as possible, the high-speed reducer adopts the traditional NGW type planetary row 15, the structure of the NGW type planetary row 15 is symmetrical, and the axial dimension of the point drive axle is reduced compactly and effectively.
Specifically, the NGW-type planetary row 15 includes an NGW-type ring gear 151, an NGW-type planetary gear 152, an NGW-type sun gear 153, and an NGW-type carrier 154; the NGW-type ring gear 151 is connected to the differential case 11 through the electromagnetic brake 16, that is, the NGW-type ring gear 151 is fixedly connected to the input end of the electromagnetic brake 16, and the differential case 11 is fixedly connected to the output end of the electromagnetic brake 16. When the electromagnetic brake 16 selectively performs an action, the NGW ring gear 151 can be engaged with and disengaged from the shifting differential case 11.
As shown in fig. 3, the NGW type planetary gear 152 is connected to the NGW type planetary gear carrier 154 through a revolute pair, the NGW type planetary gear carrier 154 is fixedly connected to the input end eccentric mechanism 135, and the input end eccentric mechanism 135 is axially and radially positioned through a bearing. The NGW type sun gear 153 is fixedly connected to the long half shaft 42 through a spline and a nut, and serves as an input end of the entire speed change differential mechanism 1 to obtain power from a prime mover.
As shown in fig. 3 and 5, one end of the double internal engagement conjugate ring gear 132 is connected to one end of the input end eccentric mechanism 135 via a bearing, and the other end is connected to one end of the output end eccentric mechanism 134 via a bearing; the other end of the input end eccentric mechanism 135 is fixedly connected with the NGW type planet carrier 154, and the other end of the output end eccentric mechanism 134 is matched with the speed change differential end cover 12 through a bearing so as to realize the axial positioning and the planetary circulation motion of the double internal meshing conjugate gear ring 132.
The output end eccentric mechanism 134 and the input end eccentric mechanism 135 are offset planet carriers.
In the present embodiment, the differential end cover 12 is connected to the differential case 11 and the output end housing 51 by bolts, and the motor end housing 52 is connected to the motor case 31 by bolts, constituting a frame portion of the entire electric drive axle, thereby constraining the degrees of freedom associated with the entire differential mechanism 1.
The double internal meshing planetary row 13 includes a double internal meshing ring gear 131, a double internal meshing conjugate ring gear 132, and a double internal meshing sun gear 133; the differential 14 includes a differential carrier 141, a differential bevel gear 142. The double-inner-meshing sun gear 133 is matched with the long half shaft 420 through a bearing to realize axial and radial positioning restraint, the double-inner-meshing sun gear 133 is fixedly connected with one end of the differential mechanism rack 141 through an axial spline and a fixing nut 143, and the other end of the differential mechanism rack 141 is connected with the output end axle housing 51 through a bearing.
The double inner meshing ring gear 131 is fixed to the differential case 11, is arranged concentrically with the output half shaft 4, and meshes with the outer side teeth of the double inner meshing conjugate ring gear 132, so that the entire double inner meshing planetary row 13 is located inside the ring gear, and the structure is more compact.
The outer teeth of the double inner-meshing conjugate gear ring 132 are engaged with the inner gear ring with large contact ratio, the inner teeth are engaged with the sun gear with large contact ratio, the inner teeth perform planetary motion around the sun gear through a bearing and an eccentric mechanism, and the eccentric mechanism at one end is fixedly connected with the high-speed NGW type planet carrier 154 to realize torque transmission. The double inner-meshing sun gear 133 is meshed with the double inner-meshing conjugate gear ring 132, and is fixedly connected with the differential frame 141 through a spline and a nut to realize transmission and distribution of power.
In the present embodiment, the NGW-type sun gear 153 is engaged with the NGW-type ring gear 151 and the NGW-type planetary gear 152, and the torque is connected to the input end eccentric mechanism 135 via the NGW-type carrier 154 and is further transmitted to the double internal engagement conjugated ring gear 132, the double internal engagement ring gear 131 is fixedly connected to the transmission differential case 11, and the double internal engagement conjugated ring gear 132 is in internal engagement transmission with the double internal engagement ring gear 131 and the double internal engagement sun gear 133, respectively. Since the double internally meshing sun gear 133 is fixedly connected to the differential carrier 141, torque is finally transmitted to the stub axle shaft 41 and the stub axle shaft 42 through the meshing transmission of the differential bevel gear 142; the output ends of the short half shaft 41 and the long half shaft 42 are flanges, and the flanges are connected with a hub through bolts to transmit torque to wheels of the vehicle so as to drive the vehicle, and differential output is realized by the differential 14 during turning.
As shown in fig. 4, the electromagnetic brake 16 is connected to the speed change differential case 11 and the NGW-type ring gear 151 to selectively fix and release the NGW-type ring gear 151; the input end 171 of the electromagnetic clutch is connected with the motor rotor 33 through a spline and can axially move under the control of an electromagnet; the output end 172 of the electromagnetic clutch is directly and fixedly connected with the NGW type carrier 154, and the NGW type carrier 154 and the motor rotor 33 can be frictionally combined and disconnected under the control of the electromagnetic clutch 17.
The working principle of the embodiment is as follows:
as shown in fig. 6, in the power-off state, the electromagnetic brake 16 brakes, the NGW-type ring gear 151 is relatively fixed, and the NGW-type sun gear 153 is connected with the motor rotor 33 as an input end; when the power is lost, the electromagnetic clutch 17 is disconnected, torque is not transmitted, the NGW type planet carrier 154 freely moves, the speed reduction ratio of the NGW type planet row 15 is i = (the number of teeth of the inner gear ring/the number of teeth of the sun gear) +1, the torque is continuously transmitted forwards, and is distributed by the speed reduction and the differential mechanism of the double inner meshing planet rows 13 to drive a wheel hub, and at this time, the wheel hub is a low-speed gear of the electric drive axle.
As shown in fig. 7, in the powered state, electromagnetic brake 16 is released, and NGW ring gear 151 is free to rotate; the NGW-type sun gear 153 is connected to the motor rotor 33 as an input end, and the electromagnetic clutch 17 is frictionally coupled when energized to transmit torque to the NGW-type carrier 154 so that the NGW-type carrier has the same rotational speed as the NGW-type sun gear 153, and since the NGW-type planetary gear set 15 has two members moving in the same manner, one member outputs and the other member freely moves, and the reduction ratio thereof is i =1. The torque is continuously transmitted forwards, is decelerated by the double internal meshing planetary row 13 and is distributed by the differential mechanism to drive the hub, and the hub is the high-speed gear of the electric drive axle.
The two-gear electric drive axle of the embodiment can realize two reduction ratios to output in a gear shifting mode by matching the clutch and the brake, thereby meeting the requirement of the vehicle on torque at different speeds and realizing effective unification of output torque performance and low energy consumption. The two-stage speed reduction structure of the embodiment adopts a high-speed stage NGW planetary gear train and a low-speed stage internally engaged planetary gear train series connection structure and a motor which are coaxially arranged, so that compared with a traditional electric drive axle, the speed reducer is more compact in structure, smaller in size and capable of realizing a larger speed reduction ratio; meanwhile, the double internal engagement planetary gear train adopts a gear with large contact ratio, and can realize more teeth to be engaged simultaneously, so that fluctuation caused by the change of the number of the engaged teeth is reduced, the running of the electric drive axle is smoother, and more engaged teeth also improve the belt load capacity of the electric drive axle.
The sectional type assembled axle housing simplifies the processing technology, improves the processing and assembling efficiency of the electric bridge, and reduces the cost of the electric bridge. The double inner meshing planetary row 13 and the NGW type planetary row 15 of the embodiment are coaxially arranged with the motor 3 and the output half shaft 4, so that the size of the speed reducer is effectively reduced, and the mechanism of the electric drive axle is more compact. The electric automobile driving device can realize two rotating speeds and torque output, is compact in structure, has better bearing capacity and transmission stability, and can be widely applied to the field of electric automobiles under various application working conditions.
Example two:
the embodiment provides a new energy automobile, installs embodiment one two grades of formula electric drive axles, long semi-axis 42, short semi-axis 41 link to each other with the wheel hub through the ring flange respectively, and output axle housing 51, motor end axle housing 52 are connected with the automobile body through damping device.
The above description is only a preferred embodiment of the present application and is not intended to limit the present application, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present application shall be included in the protection scope of the present application.
Claims (10)
1. A two-speed electric transaxle comprising:
the motor is internally provided with a long half shaft through;
the variable speed differential mechanism is detachably connected to one end of the motor and comprises an electromagnetic clutch, an NGW type planetary row and a double internal meshing planetary row which are sequentially arranged along a long half shaft, an electromagnetic brake is arranged between the NGW type planetary row and the variable speed differential shell, and one end of the long half shaft is connected with a short half shaft through a differential mechanism; different gears are switched by switching on and off the electromagnetic brake and the electromagnetic clutch.
2. The two-speed electric transaxle of claim 1 wherein the NGW-type planetary gear train comprises an NGW-type annular gear, an NGW-type planetary gear, an NGW-type sun gear, and an NGW-type planet carrier, the NGW-type sun gear being fixed to the long half shaft;
the NGW type annular gear is connected with the speed-changing differential shell through an electromagnetic brake; and the NGW type planet gear is connected with an NGW type planet carrier, and the NGW type planet carrier is fixedly connected with the input end eccentric mechanism.
3. The two-speed electric drive axle according to claim 2, wherein the electromagnetic clutch has an input connected to the motor rotor and an output connected to the NGW-type carrier.
4. The two-speed electric drive axle according to claim 1, wherein the double internally meshing planetary gear train includes a double internally meshing ring gear, a double internally meshing conjugate ring gear, and a double internally meshing sun gear, the double internally meshing sun gear being mounted to the long axle shaft through a bearing, the double internally meshing conjugate ring gear meshing with the double internally meshing ring gear and the double internally meshing sun gear, respectively.
5. The two-speed electric transaxle of claim 4 wherein the dual inner sun gear is fixedly coupled to the differential housing and the dual inner ring gear is fixedly coupled to the variable speed differential housing.
6. The two-gear electric drive axle according to claim 4, wherein one end of the double internal meshing conjugate gear ring is connected with one end of the output end eccentric mechanism through a bearing, and the other end of the output end eccentric mechanism is matched with the speed change differential end cover through a bearing; the speed change differential end cover is arranged at the end part of the speed change differential shell.
7. A two-speed electric drive axle as defined in claim 1 wherein an output axle housing is mounted outboard of said stub axle shaft, said output axle housing being removably connected to said variable speed differential housing; and a motor end axle housing is arranged on the outer side of the long half shaft and is detachably connected with the motor shell.
8. The two-speed electric drive axle according to claim 7, wherein the flange is connected to the end of the short half shaft extending out of the output axle housing and the flange is connected to the end of the long half shaft extending out of the motor axle housing.
9. A new energy automobile, characterized by comprising a two-speed electric drive axle according to any one of claims 1 to 8.
10. The new energy automobile as claimed in claim 9, wherein the axle housing of the two-gear electric drive axle is connected with the automobile body through a damping device; and the long half shaft and the short half shaft are respectively connected with the wheel hub through a flange plate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211482242.XA CN115742733A (en) | 2022-11-24 | 2022-11-24 | Two grades of formula electric transaxles and new energy automobile |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211482242.XA CN115742733A (en) | 2022-11-24 | 2022-11-24 | Two grades of formula electric transaxles and new energy automobile |
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| CN115742733A true CN115742733A (en) | 2023-03-07 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202211482242.XA Pending CN115742733A (en) | 2022-11-24 | 2022-11-24 | Two grades of formula electric transaxles and new energy automobile |
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Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20060017107A (en) * | 2004-08-20 | 2006-02-23 | 현대자동차주식회사 | A power train of an automatic transmission |
| CN201137672Y (en) * | 2007-12-28 | 2008-10-22 | 辽宁工业大学 | Double inner gearing balance type few teeth difference decelerator |
| JP2014129084A (en) * | 2014-01-20 | 2014-07-10 | Honda Motor Co Ltd | Hybrid vehicle drive device |
| CN104827898A (en) * | 2015-05-11 | 2015-08-12 | 合肥工业大学 | Two-gear speed changing power system of electric automobile |
| DE102017200531A1 (en) * | 2017-01-13 | 2018-07-19 | Zf Friedrichshafen Ag | Drivable vehicle axle and vehicle with drivable vehicle axle |
| WO2018215021A1 (en) * | 2017-05-22 | 2018-11-29 | Schaeffler Technologies AG & Co. KG | Drive device for a motor vehicle |
| CN208978607U (en) * | 2018-09-14 | 2019-06-14 | 合肥美桥汽车传动及底盘系统有限公司 | A kind of coaxial-type electric motor car driving bridge |
| CN113500904A (en) * | 2021-07-22 | 2021-10-15 | 中国北方车辆研究所 | Centralized two-gear electric drive axle |
| CN215826460U (en) * | 2021-08-11 | 2022-02-15 | 北方汤臣传动科技有限公司 | Two-gear high-speed-ratio electric drive axle structure |
| CN114523842A (en) * | 2022-03-01 | 2022-05-24 | 上海汽车变速器有限公司 | Electric drive system, electric automobile's driving system and electric automobile |
| CN114776771A (en) * | 2022-05-12 | 2022-07-22 | 中国北方车辆研究所 | One-level large-speed-ratio planetary reducer |
-
2022
- 2022-11-24 CN CN202211482242.XA patent/CN115742733A/en active Pending
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20060017107A (en) * | 2004-08-20 | 2006-02-23 | 현대자동차주식회사 | A power train of an automatic transmission |
| CN201137672Y (en) * | 2007-12-28 | 2008-10-22 | 辽宁工业大学 | Double inner gearing balance type few teeth difference decelerator |
| JP2014129084A (en) * | 2014-01-20 | 2014-07-10 | Honda Motor Co Ltd | Hybrid vehicle drive device |
| CN104827898A (en) * | 2015-05-11 | 2015-08-12 | 合肥工业大学 | Two-gear speed changing power system of electric automobile |
| DE102017200531A1 (en) * | 2017-01-13 | 2018-07-19 | Zf Friedrichshafen Ag | Drivable vehicle axle and vehicle with drivable vehicle axle |
| WO2018215021A1 (en) * | 2017-05-22 | 2018-11-29 | Schaeffler Technologies AG & Co. KG | Drive device for a motor vehicle |
| CN208978607U (en) * | 2018-09-14 | 2019-06-14 | 合肥美桥汽车传动及底盘系统有限公司 | A kind of coaxial-type electric motor car driving bridge |
| CN113500904A (en) * | 2021-07-22 | 2021-10-15 | 中国北方车辆研究所 | Centralized two-gear electric drive axle |
| CN215826460U (en) * | 2021-08-11 | 2022-02-15 | 北方汤臣传动科技有限公司 | Two-gear high-speed-ratio electric drive axle structure |
| CN114523842A (en) * | 2022-03-01 | 2022-05-24 | 上海汽车变速器有限公司 | Electric drive system, electric automobile's driving system and electric automobile |
| CN114776771A (en) * | 2022-05-12 | 2022-07-22 | 中国北方车辆研究所 | One-level large-speed-ratio planetary reducer |
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