CN114294386A - Double-speed transmission for electric automobile - Google Patents
Double-speed transmission for electric automobile Download PDFInfo
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- CN114294386A CN114294386A CN202210018660.7A CN202210018660A CN114294386A CN 114294386 A CN114294386 A CN 114294386A CN 202210018660 A CN202210018660 A CN 202210018660A CN 114294386 A CN114294386 A CN 114294386A
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 25
- 230000007246 mechanism Effects 0.000 claims description 6
- 238000004519 manufacturing process Methods 0.000 abstract description 2
- 230000009467 reduction Effects 0.000 description 4
- 230000001133 acceleration Effects 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
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Abstract
The invention discloses a double-speed transmission for an electric automobile, which comprises a first planetary gear set, a second planetary gear set, a differential, a first brake and a second brake, wherein the first planetary gear set comprises a first sun gear, a first planetary gear carrier and a first annular gear ring which are distributed from inside to outside; the first ring-shaped gear ring is fixedly connected with the second planet carrier, the first planet carrier is fixedly connected with the second sun gear, the first planet carrier is connected with the first brake, and the second planet carrier is connected with the second brake. The invention has simple structure, low manufacturing cost, higher gear shifting speed and higher transmission efficiency, and is very suitable for electric automobiles.
Description
Technical Field
The invention relates to a transmission, in particular to a double-speed transmission for an electric automobile.
Background
The electric automobile has the advantages that the driving motor has a very wide output rotating speed, and the driving corresponding speed is very high, so the traditional gearbox is not suitable for the electric automobile. At present, most of electric automobiles adopt a single-stage reduction mechanism as a transmission structure, but the mode is selected in a compromise mode based on the characteristics of wide rotating speed range, extremely high response speed and high working efficiency of a driving motor. The single-stage speed reducing mechanism has certain disadvantages, including that the electric automobile usually has low maximum speed (generally can only reach 140 plus 200KMH, which is far lower than a fuel automobile with the same power), the medium-high speed running acceleration performance is poor (the torque is reduced a lot after the rotating speed reaches a certain condition), and the medium-high speed running energy consumption is high (the actual available capacity of the battery is greatly reduced due to the larger discharging current of the battery after the rotating speed reaches a certain condition).
For the requirement of a speed reduction structure of an electric automobile, the characteristics of quick response, fewer speed change gears and very high transmission efficiency need to be realized, and meanwhile, a reversing gear can not be arranged. Based on the requirement background, if a multistage transmission structure meeting the requirements of the electric automobile can be realized, the acceleration capacity of the electric automobile in the process of traveling at the highest speed and the middle and high speed can be improved, the energy consumption of the electric automobile in the process of traveling at the high speed can be reduced, and the cruising mileage can be increased.
Disclosure of Invention
In view of the above-mentioned drawbacks of the prior art, the present invention aims to: a two-speed transmission for an electric vehicle is provided.
The technical solution of the invention is as follows: a double-speed transmission for an electric automobile comprises a first planetary gear set, a second planetary gear set, a differential, a first brake and a second brake, wherein the first planetary gear set comprises a first sun gear, a first planetary gear carrier and a first annular ring gear which are distributed from inside to outside, the first sun gear is used for being connected with a driving shaft of a driving motor, the second planetary gear set comprises a second sun gear, a second planetary gear carrier and a second annular ring gear which are distributed from inside to outside, and the second annular ring gear is used for being connected with the differential;
the first ring-shaped gear ring is fixedly connected with the second planet carrier, the first planet carrier is fixedly connected with the second sun gear, the first planet carrier is connected with the first brake, and the second planet carrier is connected with the second brake.
Furthermore, one end of the first planet carrier is rotatably connected with a first planet gear, the first planet gear is meshed with the first sun gear and the first annular gear ring, and the other end of the first planet carrier is fixed with one end of the second sun gear.
Furthermore, one end of the second planet gear carrier is rotatably connected with a second planet gear, the second planet gear is meshed with the second sun gear and the second annular gear ring, and the other end of the second planet gear carrier is fixed with one end of the first annular gear ring.
Further, the second annular ring gear is connected with the differential through a connecting frame.
Further, when one of the first brake and the second brake is in a braking state, the other is in a non-braking state.
The double-speed transmission for the electric automobile has the beneficial effects that: the gear shifting mechanism is simple in structure, low in manufacturing cost, high in gear shifting speed and high in transmission efficiency, and is very suitable for electric automobiles.
Drawings
Fig. 1 is a schematic view of the overall structure of the present invention.
Shown in the figure: 1-first planetary gear set, 11-first sun gear, 12-first planet carrier, 121-first planet gear, 13-first ring gear, 2-second planetary gear set, 21-second sun gear, 22-second planet carrier, 221-second planet gear, 23-second ring gear, 3-differential, 4-first brake, 5-second brake, 6-drive motor, 61-drive shaft, 7-connecting carrier.
Detailed Description
For a more intuitive and complete understanding of the technical solution of the present invention, the following non-limiting features are described in conjunction with the accompanying drawings of the present invention:
as shown in fig. 1, a two-speed transmission for an electric vehicle comprises a first planetary gear set 1, a second planetary gear set 2, a differential 3, a first brake 4 and a second brake 5, wherein the first planetary gear set 1 comprises a first sun gear 11, a first planet carrier 12 and a first annular ring gear 13 which are distributed from inside to outside, the first sun gear 11 is used for connecting a driving shaft 61 of a driving motor 6, the second planetary gear set 2 comprises a second sun gear 21, a second planet carrier 22 and a second annular ring gear 23 which are distributed from inside to outside, the second annular ring gear 23 is connected with the differential 3 through a connecting frame 7, and the differential 3 is used for transmitting driving force to driving wheels of the vehicle;
the first ring gear 13 is fixedly connected to the second planet carrier 22, the first planet carrier 12 is fixedly connected to the second sun gear 21, the first planet carrier 12 is connected to the first brake 4, and the second planet carrier 22 is connected to the second brake 5.
One end of the first planet carrier 12 is rotatably connected with a first planet gear 121, the first planet gear 121 is meshed with the first sun gear 11 and the first annular ring gear 13, and the other end of the first planet carrier 12 is fixed with one end of the second sun gear 21. The first sun gear 11 rotates to drive the first planetary gears 121 to rotate, and the first planetary gears 121 rotate to drive the first ring gear 13 to rotate.
One end of the second carrier 22 is rotatably connected to second planetary gears 221, the second planetary gears 221 mesh with the second sun gear 21 and the second ring gear 23, and the other end of the second carrier 22 is fixed to one end of the first ring gear 13. When the second sun gear 21 rotates, the second planet gears 221 can be driven to rotate, and the second ring-shaped gear 23 is driven to rotate after the second planet gears 221 rotate.
When one of the first brake 4 and the second brake 5 is in a braking state and the other is in a non-braking state, namely, the invention only allows one brake to be in a braking state at most, and the two-speed gear is realized by switching the states of the first brake 4 and the second brake 5.
The working principle of the invention is as follows:
when the first brake 4 is released and the second brake 5 is held, the first ring gear 13 of the first planetary gear set 1 and the second carrier 22 of the second planetary gear set 2 are in a stationary state. The first sun gear 11 of the first planetary gear set 1 is driven by the driving motor 6 to rotate in a forward direction, the first planet carrier 12 is directly connected with the second sun gear 21, and the calculation formula of the transmission ratio of the planetary gear set can calculate that the first planet carrier 12 simultaneously rotates in the forward direction and the second sun gear 21 fixedly connected with the first planet carrier also rotates in the forward direction. Meanwhile, since the second carrier 22 is in a stationary state, it can be found from the planetary gear set transmission ratio calculation formula that when the operating speed of the second carrier 22 is 0, the second sun gear 21 is operated in a forward direction to drive the second ring gear 23 to operate in a reverse direction, which is a high reduction ratio gear.
According to the calculation formula of the transmission ratio of the planetary gear set: ns + K Nr- (1+ K) Nh ═ 0
Where Ns represents sun gear speed; nr represents the ring gear rotational speed; nh represents the planet carrier speed; k represents the ring gear to sun gear tooth ratio.
When the ring gear of the first planetary gear set 1 is stationary, Nr1 is 0, so in the first planetary gear set 1 configuration Ns1- (1+ K) × Nh1 is 0, i.e., the first sun gear 11 and the first carrier 12 are in co-rotation, and the speed ratio Ns1 is (1+ K) × Nh 1. Nr1 represents the first ring gear 13 speed, Nh1 represents the first carrier 12 speed, and Ns1 represents the first sun gear 11 speed.
While the second planetary gear carrier 22, which is fixedly connected to the first ring gear 13 of the first planetary gear set 1, is stationary, Nh2 is equal to 0, so that in the second planetary gear set 2 configuration Ns2+ K Nr2 is equal to 0, i.e. the second sun gear 21 and the second ring gear 23 are running in opposite directions and the speed ratio Ns2 is equal to-K Nr 2. Nr2 represents the second ring gear 23, Nh2 represents the second carrier 22, and Ns2 represents the second sun gear 21.
Since the first carrier 12 of the first planetary gear set 1 is fixedly connected to the second sun gear 21 of the second planetary gear set 2, Nh1 is Ns 2. According to the above two formulas, when the driving motor 6 drives the first sun gear 11 of the first planetary gear set 1 to operate in the forward direction, the second ring gear 23 of the second planetary gear set 2 is finally driven to operate in the reverse direction, and the transmission ratio is
When the first brake 4 is kept braked and the second brake 5 is released, the first planet carrier 12 of the first planetary gear set 1 and the second sun gear 21 of the second planetary gear set 2 are in a stationary state. The driving motor 6 drives the first sun gear 11 of the first planetary gear set 1 to rotate in the forward direction, and the first ring gear 13 is driven to rotate in the reverse direction by the forward rotation of the first sun gear 11 of the first planetary gear set 1 according to the planetary gear set transmission ratio calculation formula, and the second planet carrier 22 connected with the first ring gear 13 synchronously rotates in the reverse direction. The second sun gear 21 of the second planetary gear set 2 remains stationary and reverse operation of the second planet carrier 22 causes reverse operation of the second ring gear 23, which is a low reduction ratio gear.
When the first carrier 12 of the first planetary gear set 1 is stationary, Nh1 is 0, then in the first planetary gear set 1 configuration Ns1+ K Nr is 0, i.e. the first sun gear 11 and the first ring gear 13 are in reverse operation, and the speed ratio is Ns 1-K Nr 1.
While the second sun gear 21 of the second planetary gear set 2, which is fixedly connected to the first carrier 12 of the first planetary gear set 1, is stationary, Ns2 is equal to 0, then in the second planetary gear set 2 configuration, K × Nr2- (1+ K) × Nh2 is equal to 0, i.e., the second carrier 22 and the second ring gear 23 are running in the same direction and the speed ratio is K × Nr2 equal to (1+ K) × Nh2.
Since the first ring gear 13 of the first planetary gear set 1 is fixedly connected to the second planet carrier 22 of the second planetary gear set 2, that is, Nr1 is nh2, it can be derived from the above two formulas that when the driving motor 6 drives the first sun gear 11 of the first planetary gear set 1 to operate in the forward direction, the second ring gear 23 of the second planetary gear set 2 is finally driven to operate in the reverse direction, and the transmission ratio is
When the vehicle needs to be backed, the driving direction of the driving motor 6 only needs to be changed, and the driving can be realized.
It should be understood that the above description is only a preferred embodiment of the present invention, and not intended to limit the scope of the present invention, and that the present invention is not limited by the above description and drawings.
Claims (5)
1. A double-speed transmission for an electric automobile is characterized in that: the brake system comprises a first planetary gear set, a second planetary gear set, a differential mechanism, a first brake and a second brake, wherein the first planetary gear set comprises a first sun gear, a first planetary gear carrier and a first annular ring gear which are distributed from inside to outside, the first sun gear is used for being connected with a driving shaft of a driving motor, the second planetary gear set comprises a second sun gear, a second planetary gear carrier and a second annular ring gear which are distributed from inside to outside, and the second annular ring gear is used for being connected with the differential mechanism;
the first ring-shaped gear ring is fixedly connected with the second planet carrier, the first planet carrier is fixedly connected with the second sun gear, the first planet carrier is connected with the first brake, and the second planet carrier is connected with the second brake.
2. The two-speed transmission for the electric vehicle as claimed in claim 1, wherein: one end of the first planet gear carrier is rotatably connected with a first planet gear, the first planet gear is meshed with the first sun gear and the first annular gear ring, and the other end of the first planet gear carrier is fixed with one end of the second sun gear.
3. The two-speed transmission for the electric vehicle as claimed in claim 1, wherein: one end of the second planet gear carrier is rotatably connected with a second planet gear, the second planet gear is meshed with the second sun gear and the second annular gear ring, and the other end of the second planet gear carrier is fixed with one end of the first annular gear ring.
4. The two-speed transmission for the electric vehicle as claimed in claim 1, wherein: the second annular gear ring is connected with the differential mechanism through a connecting frame.
5. The two-speed transmission for the electric vehicle as claimed in claim 1, wherein: when one of the first brake and the second brake is in a braking state, the other brake is in a non-braking state.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2021200777256 | 2021-01-12 | ||
| CN202110038565.9A CN112728022A (en) | 2021-01-12 | 2021-01-12 | Double-speed transmission for electric automobile |
| CN2021100385659 | 2021-01-12 | ||
| CN202120077725 | 2021-01-12 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114294386A true CN114294386A (en) | 2022-04-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210018660.7A Pending CN114294386A (en) | 2021-01-12 | 2022-01-08 | Double-speed transmission for electric automobile |
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| CN (1) | CN114294386A (en) |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4479404A (en) * | 1981-09-08 | 1984-10-30 | Stockton Thomas R | Concentric powertrain for electric vehicle |
| CN102146990A (en) * | 2011-04-27 | 2011-08-10 | 北京理工华创电动车技术有限公司 | Automatic speed changing system of electric automobile |
| CN102162505A (en) * | 2011-04-27 | 2011-08-24 | 北京理工华创电动车技术有限公司 | Planet gear type automatic speed change system for electric automobile |
| KR20120097709A (en) * | 2011-02-25 | 2012-09-05 | 현대 파워텍 주식회사 | Speed reduction apparatus for vehicles |
| CN103363034A (en) * | 2013-08-01 | 2013-10-23 | 南宁市坤捷机电设备制造有限公司 | Automatic speed changer for multifunctional garbage electric car |
| CN105673783A (en) * | 2016-04-21 | 2016-06-15 | 中国北方车辆研究所 | Large-transmission-ratio two-gear planetary transmission |
| CN105736654A (en) * | 2016-04-20 | 2016-07-06 | 长安大学 | Two-stage gearbox of electric vehicle |
| CN106939929A (en) * | 2017-05-19 | 2017-07-11 | 福建万润新能源科技有限公司 | A kind of shift transmission of mono-tooth ring dry friction external control three |
| CN108050222A (en) * | 2017-12-08 | 2018-05-18 | 合肥工业大学 | One kind two keeps off electric vehicle power-driven system |
| CN108131427A (en) * | 2017-12-27 | 2018-06-08 | 合肥工业大学 | A kind of 2 speed automatic transmissions and shifting control system |
| US20180216709A1 (en) * | 2017-02-01 | 2018-08-02 | Neooto Co., Ltd. | Two-speed transmission for electric vehicle |
| CN112728022A (en) * | 2021-01-12 | 2021-04-30 | 花潍 | Double-speed transmission for electric automobile |
-
2022
- 2022-01-08 CN CN202210018660.7A patent/CN114294386A/en active Pending
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4479404A (en) * | 1981-09-08 | 1984-10-30 | Stockton Thomas R | Concentric powertrain for electric vehicle |
| KR20120097709A (en) * | 2011-02-25 | 2012-09-05 | 현대 파워텍 주식회사 | Speed reduction apparatus for vehicles |
| CN102146990A (en) * | 2011-04-27 | 2011-08-10 | 北京理工华创电动车技术有限公司 | Automatic speed changing system of electric automobile |
| CN102162505A (en) * | 2011-04-27 | 2011-08-24 | 北京理工华创电动车技术有限公司 | Planet gear type automatic speed change system for electric automobile |
| CN103363034A (en) * | 2013-08-01 | 2013-10-23 | 南宁市坤捷机电设备制造有限公司 | Automatic speed changer for multifunctional garbage electric car |
| CN105736654A (en) * | 2016-04-20 | 2016-07-06 | 长安大学 | Two-stage gearbox of electric vehicle |
| CN105673783A (en) * | 2016-04-21 | 2016-06-15 | 中国北方车辆研究所 | Large-transmission-ratio two-gear planetary transmission |
| US20180216709A1 (en) * | 2017-02-01 | 2018-08-02 | Neooto Co., Ltd. | Two-speed transmission for electric vehicle |
| CN106939929A (en) * | 2017-05-19 | 2017-07-11 | 福建万润新能源科技有限公司 | A kind of shift transmission of mono-tooth ring dry friction external control three |
| CN108050222A (en) * | 2017-12-08 | 2018-05-18 | 合肥工业大学 | One kind two keeps off electric vehicle power-driven system |
| CN108131427A (en) * | 2017-12-27 | 2018-06-08 | 合肥工业大学 | A kind of 2 speed automatic transmissions and shifting control system |
| CN112728022A (en) * | 2021-01-12 | 2021-04-30 | 花潍 | Double-speed transmission for electric automobile |
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