CN110725910B - New energy commercial vehicle EAT derailleur gear drive structure - Google Patents
New energy commercial vehicle EAT derailleur gear drive structure Download PDFInfo
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- CN110725910B CN110725910B CN201810784516.8A CN201810784516A CN110725910B CN 110725910 B CN110725910 B CN 110725910B CN 201810784516 A CN201810784516 A CN 201810784516A CN 110725910 B CN110725910 B CN 110725910B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
Abstract
The invention discloses a new energy commercial vehicle EAT transmission gear transmission structure, which comprises a front end sun wheel, a front end planet wheel, a rear end sun wheel and a rear end primary planet wheel, the front end sun wheel is meshed with the front end planet wheel, the rear end planet wheel and the front end planet wheel are arranged on the same rotating shaft, the rear end planet wheel is meshed with the rear end planet wheel and the inner gear ring respectively, the front end sun wheel, the rear end sun wheel and the inner gear ring are in axis coincidence, the rear end planet wheel is meshed with the rear end sun wheel and the inner gear ring respectively, the front end planet wheel, the rear end planet wheel and the rear end planet wheel are mounted on the planet carrier, the rear end sun wheel is connected with the input shaft, the planet carrier is connected with the output shaft, a clutch is arranged between the input shaft and the planet carrier, the inner gear ring is provided with a first brake, and the front end sun wheel is provided with a second brake. The invention has the advantages of simple structure, low cost, compact structure and the like.
Description
Technical Field
The invention relates to the field of new energy commercial vehicles, in particular to a highway passenger car 8-12 m long, and particularly discloses a gear transmission structure of an EAT transmission of a new energy commercial vehicle.
Background
A conventional AT Transmission (Automatic Transmission) generally includes a torque converter, a planetary gear train, a plurality of friction engagement elements, and a corresponding electronic control system, and is widely applied to the field of passenger cars, because power shifting is realized by separating and combining the friction engagement elements. However, in the field of new energy commercial vehicles (electric drive commercial vehicles), an MT transmission (manual transmission) and an AMT transmission (mechanical automatic transmission) are mainly adopted, and AT present, there is no AT transmission applied in batch. In order to improve the power transmission performance of a fuel engine, reduce fuel consumption, shift smoothness and the like of the traditional AT transmission, the number of set gears is large, the transmission ratio is large (more than 6), and because an output shaft of the fuel engine can only rotate in a single direction and must be set with a reverse gear, the structure of a gear transmission system is very complex, the manufacturing cost is increased, and the size of the transmission is increased. And new forms of energy commercial vehicle gear number is less, only need set up two usually to three the fender can, the drive ratio is corresponding also lower, simultaneously because the motor both can the forward rotation can the antiport, therefore need not to require the derailleur to have the reverse gear for traditional AT derailleur gear drive structure no longer is applicable to new forms of energy commercial vehicle.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a new energy commercial vehicle transmission gear transmission structure which is simple in structure, low in cost and compact in structure.
In order to solve the technical problems, the invention adopts the following technical scheme:
an EAT transmission gear transmission structure of a new energy commercial vehicle comprises a front end sun wheel, a front end planet wheel, a rear end sun wheel, a rear end primary planet wheel, a rear end secondary planet wheel, a planet carrier and an inner gear ring, wherein the front end sun wheel is meshed with the front end planet wheel, the rear end primary planet wheel and the front end planet wheel are arranged on the same rotating shaft, the rear end primary planet wheel is respectively meshed with the rear end secondary planet wheel and the inner gear ring, the axle centers of the front end sun wheel, the rear end sun wheel and the inner gear ring are coincident, the rear end secondary planet wheel is respectively meshed with the rear end sun wheel and the inner gear ring, the front end planet wheel, the rear end primary planet wheel and the rear end secondary planet wheel are arranged on the planet carrier, the rear end sun wheel is connected with an input shaft, and the planet carrier is connected with an output shaft, a clutch is arranged between the input shaft and the planet carrier, the inner gear ring is provided with a first brake, and the front end sun gear is provided with a second brake.
As a further improvement of the above technical solution: the gear transmission structure has a first transmission ratio i1When the first brake is operated and the second brake and the clutch are not operated, i1＝1+k2Wherein k is2The gear ratio of the inner gear ring to the rear end sun gear is obtained.
As a further improvement of the above technical solution: i is not less than 41≤5。
As a further improvement of the above technical solution: the gear transmission structure has a second transmission ratio i2When the second brake is operated and the first brake and the clutch are not operated, i2＝(k1+k2)/k1Wherein k is1Is the gear ratio of the inner gear ring to the front end sun gear, and k1≠k2。
As a further improvement of the above technical solution: 1 < i2≤3。
As a further improvement of the above technical solution: the gear transmission structure has a third transmission ratio i3When the clutch is operated and the first brake and the second brake are not operated, i3＝1。
As a further improvement of the above technical solution: the front end sun wheel, the front end planet wheel, the rear end primary planet wheel, the rear end secondary planet wheel, the rear end sun wheel and the inner gear ring are all of helical tooth structures.
As a further improvement of the above technical solution: the number of the rear-end primary planet wheels, the rear-end secondary planet wheels and the front-end planet wheels is n, and n is more than or equal to 3.
As a further improvement of the above technical solution: the planet carrier is of a hollow sleeve structure and is positioned in the inner gear ring, the rear-end primary planet wheel, the rear-end secondary planet wheel and the front-end planet wheel are positioned in a cavity of the planet carrier, a first opening through which the gear teeth penetrate is formed in the side wall of the planet carrier, and second openings through which the input shaft and the output shaft penetrate are formed in the two ends of the planet carrier respectively.
Compared with the prior art, the invention has the advantages that: the invention discloses a new energy commercial vehicle EAT transmission gear transmission structure, wherein the front end adopts a double-stage planetary gear set, the rear end adopts a single-stage planetary gear set, a front-end planetary gear and a rear-end planetary gear are arranged on the same rotating shaft, two planetary gear sets share a planetary carrier and an inner gear ring, a rear-end sun gear is connected with an input shaft, the planetary carrier is connected with an output shaft, a clutch is arranged between the input shaft and the planetary carrier, the inner gear ring is provided with a first brake, the front-end sun gear is provided with a second brake, three forward gears can be realized through the matching of the clutch, the first brake and the second brake, reverse gear can be realized through the reverse rotation of a driving motor, different transmission ratios can be obtained through reasonably adjusting the tooth number of the inner gear ring, the tooth number of the front-end sun gear and the tooth number of the rear-end sun gear, the requirements of a new energy passenger vehicle with the length of 8-12 m can be met, and the integral structure is simple, Compact, spare part is few, shows through the trial-and-error: compared with a parallel shaft type transmission with a traditional structure capable of realizing the same function, the transmission can be reduced in size by about 1/3.
Drawings
FIG. 1 is a schematic perspective structure diagram of a first view angle of a gear transmission structure of an EAT transmission of a new energy commercial vehicle.
FIG. 2 is a perspective view of a second perspective of the EAT transmission gearing structure of the new energy commercial vehicle of the present invention.
Fig. 3 is a perspective view of fig. 1.
Fig. 4 is a schematic diagram of the first gear transmission of the present invention.
Fig. 5 is a schematic diagram of the second gear transmission of the present invention.
Fig. 6 is a schematic diagram of the three-gear transmission of the present invention.
The reference numerals in the figures denote: 1. a rear sun gear; 2. a rear-end primary planet wheel; 3. a rear-end secondary planet wheel; 4. a front end sun gear; 5. a front end planet wheel; 6. a planet carrier; 61. a first opening; 62. a second opening; 7. an inner gear ring; 8. an input shaft; 9. an output shaft; 10. a clutch; 11. a first brake; 12. and a second brake.
Detailed Description
The invention is described in further detail below with reference to the figures and specific examples of the specification.
Fig. 1 to 3 show an embodiment of a new energy commercial vehicle EAT transmission gear transmission structure of the present invention, which includes a rear end sun gear 1, a rear end primary planet gear 2, a rear end secondary planet gear 3, a front end sun gear 4, a front end planet gear 5, a planet carrier 6 and an inner gear ring 7, wherein the rear end secondary planet gear 3 is respectively engaged with the rear end sun gear 1 and the inner gear ring 7, the front end planet gear 5 and the rear end primary planet gear 2 are arranged on the same rotation axis, the axes of the rear end sun gear 1, the inner gear ring 7 and the front end sun gear 4 are coincident, the front end planet gear 5 is engaged with the front end sun gear 4 and then respectively engaged with the rear end secondary planet gear 3 and the inner gear ring 7 through the rear end primary planet gear 2, the rear end secondary planet gear 3 and the front end planet gear 5 are mounted on the planet carrier 6, the rear end sun gear 1 is connected with an input shaft 8, the planet carrier 6 is connected with an output shaft 9, a clutch 10 is arranged between the input shaft 8 and the planet carrier 6, the inner gear ring 7 is provided with a first brake 11, and the front end sun gear 4 is provided with a second brake 12.
The EAT speed changer gear transmission structure of the new energy commercial vehicle adopts a double-stage planetary gear set at the front end, a single-stage planetary gear set at the rear end, a front-end planetary gear 5 and a rear-end planetary gear 2 which are arranged on the same rotating shaft, a planetary carrier 6 and an inner gear ring 7 which are shared by the two planetary gear sets, a rear-end sun gear 1 connected with an input shaft 8, the planetary carrier 6 connected with an output shaft 9, a clutch 10 arranged between the input shaft 8 and the planetary carrier, a first brake 11 arranged on the inner gear ring 7, a second brake 12 arranged on the front-end sun gear 4, three forward gears can be realized through the cooperation of the clutch 10, the first brake 11 and the second brake 12, reverse gear can be realized through the reverse rotation of a vehicle driving motor, different transmission ratios can be obtained through reasonably adjusting the tooth number of the inner gear ring 7, the tooth number of the front-end sun gear 4 and the tooth number of the rear-end sun gear 1, so as to meet the requirements of a new energy passenger vehicle with the length of 8 m-12 m, and overall structure is simple, compact, and spare part is small in quantity, shows through the trial-manufacture: compared with a parallel shaft type transmission with a traditional structure capable of realizing the same function, the transmission can reduce the size of the transmission by about 1/3, greatly reduce the occupation of vehicle space and facilitate the layout of other components of the vehicle, particularly battery packs. The clutch 10, the first brake 11 and the second brake 12 may be implemented by using an existing structure, and will not be described in detail.
Specifically, as shown in fig. 4 (in which arrows indicate power transmission paths, x indicates a non-operating state, and v indicates an operating state, the same applies hereinafter), further, in the present embodiment, the gear transmission structure has a first transmission ratio i1When the first brake 11 is operated and the second brake 12 and the clutch 10 are not operated, i1＝1+k2Wherein k is2The gear ratio of the inner gear ring 7 to the rear end sun gear 1 is shown.
In this condition, power is input from the input shaft 8 to the rear sun gear 4, and power is directly output from the carrier 6 at this time because the ring gear 7 is locked.
As a preferred technical solution, i is more than or equal to 41Less than or equal to 5, and the first gear speed ratio requirement of the new energy commercial vehicle can be better met. In this example, k2A value of 3.5, correspondingly, i14.5. Of course, in other embodiments, the adjustment can be performed according to different users and different use environments of the vehicle.
Further, in the present embodiment, the gear transmission structure has a second transmission ratio i as shown in fig. 52When the second brake 12 is operated and the first brake 11 and the clutch 10 are not operated, i2＝(k1+k2)/k1Wherein k is1Is the gear ratio of the inner gear ring 7 and the front end sun gear 4, and k1≠k2。
In this condition, power is input from the input shaft 8 to the rear sun gear 1, and since the front sun gear 4 is locked, power is transmitted through the two-stage planetary rows and then output from the carrier 6.
As a preferred technical scheme, 1 < i2Less than or equal to 3, and can better meet the speed ratio requirement of the second gear of the commercial vehicle with new energy. In this example, k1A value of 1.9, k2A value of 3.5, correspondingly, i12.84. Of course, in other embodiments, the adjustment can be performed according to different users and different use environments of the vehicle.
Further, as shown in FIG. 6, in the present embodiment, the gear transmission structure has a third transmission ratio i3When the clutch 10 is operated and the first brake 11 and the second brake 12 are not operated, i3＝1。
In this condition, the input shaft 8 is connected with the planet carrier 6, so that the power is directly output through the planet carrier 6 and is used as a direct gear of the new energy commercial vehicle.
Further, in this embodiment, the front-end sun gear 4, the front-end planet gear 5, the rear-end primary planet gear 2, the rear-end secondary planet gear 3, the rear-end sun gear 1, and the inner gear ring 7 are all of helical gear structures. The helical gear has good meshing performance, stable transmission and low noise, reduces the load of each pair of gears and improves the bearing capacity of the gears.
As an optimal technical scheme, the number of the rear-end primary planet wheels 2, the rear-end secondary planet wheels 3 and the front-end planet wheels 5 is n, and n is larger than or equal to 3, namely the sun wheel is matched with 2-3 planet wheels, so that the structure is simple and compact, and the transmission requirement is met.
As a preferred technical solution, in this embodiment, the planet carrier 6 is a hollow sleeve structure and is located in the ring gear 7, the rear-end primary planet gear 2, the rear-end secondary planet gear 3, and the front-end planet gear 5 are located in a cavity of the planet carrier 6, a first opening 61 through which the gear teeth pass is formed in a side wall of the planet carrier 6, and second openings 62 through which the input shaft 8 and the output shaft 9 pass are formed in two ends of the planet carrier 6, respectively. The planet carrier 6 has simple and compact structure and small occupied space, and simultaneously meets the requirements of installation and meshing of various planet wheels and rotating shafts.
Although the present invention has been described with reference to the preferred embodiments, it is not intended to be limited thereto. Those skilled in the art can make numerous possible variations and modifications to the present invention, or modify equivalent embodiments to equivalent variations, without departing from the scope of the invention, using the teachings disclosed above. Therefore, any simple modification, equivalent change and modification made to the above embodiments according to the technical spirit of the present invention should fall within the protection scope of the technical scheme of the present invention, unless the technical spirit of the present invention departs from the content of the technical scheme of the present invention.
Claims (9)
1. The utility model provides a new energy commercial car EAT derailleur gear drive structure which characterized in that: comprises a front end sun wheel (4), a front end planet wheel (5), a rear end sun wheel (1), a rear end primary planet wheel (2), a rear end secondary planet wheel (3), a planet carrier (6) and an inner gear ring (7), wherein the axes of the front end sun wheel (4), the rear end sun wheel (1) and the inner gear ring (7) are superposed, the front end sun wheel (4) is meshed with the front end planet wheel (5), the rear end primary planet wheel (2) and the front end planet wheel (5) are arranged on the same rotating shaft, the rear end primary planet wheel (2) is respectively meshed with the rear end secondary planet wheel (3) and the inner gear ring (7), the rear end secondary planet wheel (3) is respectively meshed with the rear end sun wheel (1) and the inner gear ring (7), the front end planet wheel (5), the rear end primary planet wheel (2) and the rear end secondary planet wheel (3) are arranged on the planet carrier (6), input shaft (8) is connected in rear end sun gear (1), output shaft (9) is connected in planet carrier (6), input shaft (8) with be equipped with clutch (10) between planet carrier (6), ring gear (7) dispose first stopper (11), front end sun gear (4) dispose second stopper (12), planet carrier (6) are hollow sleeve structure and are located in ring gear (7), rear end one-level planet wheel (2), rear end second grade planet wheel (3) and front end planet wheel (5) are located in the cavity of planet carrier (6), offer first trompil (61) that supply the teeth of a cogwheel to pass on planet carrier (6) lateral wall, offer respectively at planet carrier (6) both ends and supply input shaft (8) with second trompil (62) that output shaft (9) passed.
2. The new energy commercial vehicle EAT transmission gear transmission structure of claim 1, characterized in that: the gear transmission structure has a first transmission ratio i1When the first brake (11) is operated and the second brake (12) and the clutch (10) are not operated, i1＝1+k2Wherein k is2The gear ratio of the inner gear ring (7) to the rear end sun gear (1) is adopted.
3. The new energy commercial vehicle EAT transmission gearing structure according to claim 2, characterized in that: i is not less than 41≤5。
4. The new energy commercial vehicle EAT transmission gearing structure according to claim 2, characterized in that: the gear transmission structure has a second transmission ratio i2When the second brake (12) is operated and the first brake (11) and the clutch (10) are not operated, i2＝(k1+k2)/k1Wherein k is1Is the gear ratio of the inner gear ring (7) to the front end sun gear (4) and k1≠k2。
5. The new energy commercial vehicle EAT transmission gearing structure according to claim 4, characterized in that: 1 < i2≤3。
6. The new energy commercial vehicle EAT transmission gearing structure according to claim 4, characterized in that: the gear transmission structure has a third transmission ratio i3When the clutch (10) is operated and the first brake (11) and the second brake (12) are not operated, i3＝1。
7. The new energy commercial vehicle EAT transmission gearing structure according to any of claims 1 to 6, characterized in that: the front-end sun gear (4), the front-end planet gear (5), the rear-end primary planet gear (2), the rear-end secondary planet gear (3), the rear-end sun gear (1) and the inner gear ring (7) are all of helical tooth structures.
8. The new energy commercial vehicle EAT transmission gearing structure according to any of claims 1 to 6, characterized in that: the number of the rear-end primary planet wheels (2), the rear-end secondary planet wheels (3) and the front-end planet wheels (5) is n, and n is larger than or equal to 3.
9. The new energy commercial vehicle EAT transmission gear transmission structure of claim 8, wherein: the number of the rear-end primary planet wheels (2), the rear-end secondary planet wheels (3) and the front-end planet wheels (5) is n, and n is larger than or equal to 3.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810784516.8A CN110725910B (en) | 2018-07-17 | 2018-07-17 | New energy commercial vehicle EAT derailleur gear drive structure |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201810784516.8A CN110725910B (en) | 2018-07-17 | 2018-07-17 | New energy commercial vehicle EAT derailleur gear drive structure |
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| CN110725910A CN110725910A (en) | 2020-01-24 |
| CN110725910B true CN110725910B (en) | 2022-03-29 |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112728019A (en) * | 2021-01-13 | 2021-04-30 | 深圳市恒驱电机股份有限公司 | Motor with built-in gear difference planetary gear box |
| CN112728020A (en) * | 2021-01-15 | 2021-04-30 | 深圳市恒驱电机股份有限公司 | Motor with novel tooth difference planet wheel gear box |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103052522A (en) * | 2010-08-24 | 2013-04-17 | 大众汽车有限公司 | Hybrid drive system for a motor vehicle |
| CN103925345A (en) * | 2014-04-30 | 2014-07-16 | 北京航空航天大学 | Electric driving planetary transmission |
| CN103939539A (en) * | 2014-04-30 | 2014-07-23 | 北京航空航天大学 | Electrically-driven planetary transmission |
| CN104675933A (en) * | 2013-11-27 | 2015-06-03 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicles |
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2018
- 2018-07-17 CN CN201810784516.8A patent/CN110725910B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103052522A (en) * | 2010-08-24 | 2013-04-17 | 大众汽车有限公司 | Hybrid drive system for a motor vehicle |
| CN104675933A (en) * | 2013-11-27 | 2015-06-03 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicles |
| CN103925345A (en) * | 2014-04-30 | 2014-07-16 | 北京航空航天大学 | Electric driving planetary transmission |
| CN103939539A (en) * | 2014-04-30 | 2014-07-23 | 北京航空航天大学 | Electrically-driven planetary transmission |
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