CN107120396B - Three-stage planetary gear train automatic transmission - Google Patents
Three-stage planetary gear train automatic transmission Download PDFInfo
- Publication number
- CN107120396B CN107120396B CN201710442155.4A CN201710442155A CN107120396B CN 107120396 B CN107120396 B CN 107120396B CN 201710442155 A CN201710442155 A CN 201710442155A CN 107120396 B CN107120396 B CN 107120396B
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- China
- Prior art keywords
- gear
- clutch
- planetary gear
- brake
- transmission
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Classifications
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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
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
Abstract
The present invention relates to a three-stage planetary gear train automatic transmission for a vehicle, which is capable of achieving eight forward gears and one reverse gear, and which includes a housing, three planetary gear sets and a plurality of transmission shafts, and six coupling elements. Each planetary gear set comprises a sun gear, planet gears and a gear ring, two planetary gear sets on two sides of the planetary gear set are single-planetary gear sets, the middle planetary gear set is a double-planetary gear set, and the combining elements are selectively combined and separated in the gear shifting process to realize different transmission ratios, so that the transmission realizes eight forward gears and one reverse gear. The two planetary gear sets share one planetary gear and the six coupling elements to be matched with each other, so that excessive coupling elements are not needed, the gear shifting performance is improved, the quality and the volume of the transmission are reduced, and the dynamic performance and the transmission efficiency of the transmission are improved.
Description
Technical Field
The invention belongs to the technical field of vehicle transmission, and particularly relates to an eight-gear planetary gear transmission.
Background
In order to improve the power performance, economy and gear shifting performance of a vehicle, increase the number of gears, expand the speed ratio range, reduce the speed ratio interval, the existing transmission has achieved some purposes, but basically, the size and the quality of the transmission are reduced, and the problem cannot be fundamentally solved, so that a low-cost, compact and novel-structure multi-gear automatic transmission is required to be studied in the field.
Disclosure of Invention
The invention aims to provide an eight-gear automatic transmission of a three-stage planetary gear train for a vehicle, which utilizes three planetary rows and fewer coupling elements, and simultaneously, the coupling elements are selectively coupled and decoupled in a gear shifting process to realize different transmission ratios, so that the transmission realizes eight forward gears and one reverse gear, and is more compact and efficient.
In order to achieve the above purpose, the technical scheme of the invention is as follows: it comprises a housing 17, a first planetary gear set 100, a second planetary gear set 200 and a third planetary gear set 300, an input shaft 15, an output shaft 16, a first clutch 9, a second clutch 10, a third clutch 11 and a fourth clutch 12, and a first brake 13 and a second brake 14.
The first planetary gear set 100 is a single-row planetary gear including a first ring gear 1, a first planetary gear 2, and a first sun gear 3.
The second planetary gear set 200 is a double-row planetary gear set including a second planetary gear 5, a third planetary gear 6 and a second sun gear 8, and the second planetary gear 2 is connected with the third planetary gear 6 through a planetary carrier 18.
The third planetary gear set 300 is a single row of planet gears including the second ring gear 4, the second planet gears 5 and the third sun gear 7.
The planet carrier 18 is connected with the transmission housing 17 through the first brake 13, the second ring gear 4 is connected with the transmission housing 17 through the second brake 14, the first planet wheel 2 is connected with the planet carrier 18 through the first clutch 9, the first sun wheel 3 is connected with the planet carrier 18 through the second clutch 10, the first planet wheel 2 is connected with the second sun wheel 8 through the third clutch 11 and the first clutch 9, and the first sun wheel 3 is connected with the second sun wheel 8 through the fourth clutch 12.
In the embodiment of the invention, the input shaft 15 is continuously interconnected with the first sun gear 3 as a transmission fixed input.
In the embodiment of the invention, the output shaft 16 is continuously interconnected with the third sun gear 7 as a transmission fixed output.
In an embodiment of the invention, the first ring gear (1) is continuously interconnected with the transmission housing (17).
At least two of the six coupling elements are selectively coupled during a gear shift process to establish eight forward gears and one reverse gear between the input and output terminals of the transmission.
In the invention, the transmission establishes eight forward gears and one reverse gear, specifically:
when the second clutch 10, the fourth clutch 12 and the second brake 14 are combined, the planet carrier 18 and the second sun gear 8 rotate together, the second gear ring 4 is braked, and reverse gear is realized;
when the fourth clutch 12 and the second brake 14 are combined, the input shaft 15 drives the second sun gear 8 to rotate, and the second gear ring 4 is braked to realize first gear;
when the fourth clutch 12 is combined with the first brake 13, the second sun gear 8 drives the second planet gear 5 and the third planet gear 6 to synchronously rotate, and the planet carrier 18 brakes to realize second gear;
when the first clutch 9 and the fourth clutch 12 are combined, the first planet wheel 2 drives the planet carrier 18 to rotate, so that third gear is realized;
when the first clutch 9, the third clutch 11 and the second brake 14 are combined, the first planet wheel 2 drives the planet carrier 18 and the second sun wheel 8 to rotate, so that fourth gear is realized;
when the second clutch 10 and the second brake 14 are combined, the first planet gears 2 drive the planet carrier 18 to rotate, and the second gear ring 4 is braked to realize fifth gear;
when the second clutch 10 and the fourth clutch 12 are combined, the input shaft 15 drives the planet carrier 18 and the second sun gear 8 to rotate, so that sixth gear is realized;
when the fourth clutch 12 and the first brake 13 are combined, the input shaft 15 drives the second sun gear 8 to rotate, and the planet carrier 18 brakes to realize seventh gear;
when the second clutch 10, the third clutch (11) and the second brake 14 are combined, the input shaft 15 drives the planet carrier 18 to rotate, and the second gear ring 4 is braked to realize eighth gear;
the invention has the beneficial effects that: according to the three-stage planetary gear train automatic transmission, three planetary gear sets are arranged, wherein the second planetary gear set and the third planetary gear set share the planetary gears, so that the size and the mass of the transmission are reduced, more transmission gears are realized by fewer combination elements, the speed ratio range of the transmission is enlarged, the speed ratio interval is reduced, and the gear shifting performance of the transmission is greatly improved.
Drawings
FIG. 1 is a lever diagram of an automatic transmission of a three-stage planetary gear train of the present invention.
FIG. 2 is a schematic diagram of an automatic transmission of a three-stage planetary gear train of the present invention.
The text labels in the figures are expressed as: 1 is a first gear ring, 2 is a first planet wheel, 3 is a first sun wheel, 4 is a second gear ring, 5 is a second planet wheel, 6 is a third planet wheel, 7 is a third sun wheel, 8 is a second sun wheel, 9 is a first clutch, 10 is a second clutch, 11 is a third clutch, 12 is a fourth clutch, 13 is a first brake, 14 is a second brake, 15 is an input shaft, 16 is an output shaft, 17 is a housing, 18 is a planet carrier, 100 is a first planetary gear set, 200 is a second planetary gear set, and 300 is a third planetary gear set.
Detailed Description
In order that those skilled in the art may better understand the technical solutions of the present invention, the following detailed description of the present invention with reference to the accompanying drawings is provided for exemplary and explanatory purposes only and should not be construed as limiting the scope of the present invention.
Fig. 1 is a layout and connection of the various components of the transmission, in the form of a lever diagram, of a three-stage planetary gear automatic transmission of the present invention, which includes a housing (17), a first planetary gear set (100), second planetary gear set (200) and third planetary gear set (300), an input shaft (15), an output shaft (16), a first clutch (9), a second clutch (10), a third clutch (11) and fourth clutch (12), and a first brake (13) and a second brake (14).
The first planetary gear set (100) is a single-row planetary gear, and comprises a first gear ring (1), a first planetary gear (2) and a first sun gear (3), the second planetary gear set (200) is a double-planetary gear row, and comprises a second planetary gear (5), a third planetary gear (6) and a second sun gear (8), the second planetary gear (2) is connected with the third planetary gear (6) through a planet carrier (18), the third planetary gear set (300) is a single-row planetary gear row, and comprises a second gear ring (4), a second planetary gear (5) and a third sun gear (7), the first gear ring (1) is fixedly connected with a transmission shell (17), and the third sun gear (7) is fixedly connected with an output shaft (16) and is arranged as a fixed output end of the transmission.
The second planetary gear set (200) and the third planetary gear set (300) are connected by a common second planetary gear (5).
Arrangement of the coupling elements:
the planet carrier (18) is connected with the transmission shell (17) through a first brake (13), the second gear ring (4) is connected with the transmission shell (17) through a second brake (14), the first planet wheel (2) is connected with the planet carrier (18) through a first clutch (9), the first sun wheel (3) is connected with the planet carrier (18) through a second clutch (10), the first planet wheel (2) is connected with the second sun wheel (8) through a third clutch (11) and the first clutch (9), and the first sun wheel (3) is connected with the second sun wheel (8) through a fourth clutch (12).
The realization method of each gear comprises the following steps:
referring to fig. 1 and table 1, eight forward gears and one reverse gear, including two overdrive gears, are achieved by two or three of the coupling members for each gear. Table 1 is a table representing the states of various gear engagement elements and various gear ratios of a three-stage planetary gear automatic transmission, each gear ratio representing the ratio of input speed to output speed for each gear, which are exemplary only and which may be widely adjusted, wherein "v" represents the engagement of the engagement elements.
TABLE 1
When the second clutch (10), the fourth clutch (12) and the second brake (14) are combined, the planet carrier (18) and the second sun gear (8) rotate together, and the second gear ring (4) is braked to realize reverse gear;
when the fourth clutch (12) and the second brake (14) are combined, the input shaft (15) drives the second sun gear (8) to rotate, and the second gear ring (4) is braked to realize first gear;
when the fourth clutch (12) is combined with the first brake (13), the second sun gear (8) drives the second planet gear (5) and the third planet gear (6) to synchronously rotate, and the planet carrier (18) is braked to realize second gear;
when the first clutch (9) and the fourth clutch (12) are combined, the first planet wheel (2) drives the planet carrier (18) to rotate, so that third gear is realized;
when the first clutch (9), the third clutch (11) and the second brake (14) are combined, the first planet wheel (2) drives the planet carrier (18) and the second sun wheel (8) to rotate, so that fourth gear is realized;
when the second clutch (10) and the second brake (14) are combined, the first planet wheel (2) drives the planet carrier (18) to rotate, and the second gear ring (4) is braked to realize fifth gear;
when the second clutch (10) and the fourth clutch (12) are combined, the input shaft (15) drives the planet carrier (18) and the second sun gear (8) to rotate, so that a sixth gear is realized;
when the fourth clutch (12) is combined with the first brake (13), the input shaft (15) drives the second sun gear (8) to rotate, and the planet carrier (18) is braked to realize seventh gear;
when the second clutch (10), the third clutch (11) and the second brake (14) are combined, the input shaft (15) drives the planet carrier (18) to rotate, and the second gear ring (4) is braked, so that eighth gear is realized.
It should be noted that, in this document, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus.
The principles and embodiments of the present invention have been described herein with reference to specific examples, the description of which is intended only to facilitate an understanding of the method of the present invention and its core ideas. The foregoing is merely illustrative of the preferred embodiments of this invention, and it is noted that there is objectively no limit to the specific structure disclosed herein, since numerous modifications, adaptations and variations can be made by those skilled in the art without departing from the principles of the invention, and the above-described features can be combined in any suitable manner; such modifications, variations and combinations, or the direct application of the inventive concepts and aspects to other applications without modification, are contemplated as falling within the scope of the present invention.
Claims (1)
1. An automatic transmission of a three-stage planetary gear train comprises an input shaft (15), an output shaft (16) and a shell (17); characterized in that it further comprises a first brake (13), a second brake (14), a first planetary gear set (100), a second planetary gear set (200) and a third planetary gear set (300);
the first planetary gear set (100) and the third planetary gear set (300) are single-row planetary gears;
the second planetary gear set (200) is a double-row planetary gear, and the second planetary gear set (200) is arranged between the first planetary gear set (100) and the third planetary gear set (300);
the planet carrier (18) is connected with the transmission shell (17) through a first brake (13);
the second ring gear (4) is connected with the transmission housing (17) through a second brake (14);
the first planet wheel (2) is connected with the planet carrier (18) through a first clutch (9), the first sun wheel (3) is connected with the planet carrier (18) through a second clutch (10), the first planet wheel (2) is connected with the second sun wheel (8) through a third clutch (11) and the first clutch (9), and the first sun wheel (3) is connected with the second sun wheel (8) through a fourth clutch (12);
the input shaft (15) is fixedly interconnected with the first sun gear (3); the third sun gear (7) is fixedly interconnected with the output shaft (16);
the transmission establishes eight forward gears and one reverse gear, specifically:
when the second clutch (10), the fourth clutch (12) and the second brake (14) are combined, the planet carrier (18) and the second sun gear (8) rotate together, and the second gear ring (4) is braked to realize reverse gear;
when the fourth clutch (12) and the second brake (14) are combined, the input shaft (15) drives the second sun gear (8) to rotate, and the second gear ring (4) is braked to realize a first gear;
when the fourth clutch (12) is combined with the first brake (13), the second sun gear (8) drives the second planet gear (5) and the third planet gear (6) to synchronously rotate, and the planet carrier (18) is braked to realize a second gear;
when the first clutch (9) and the fourth clutch (12) are combined, the first planet wheel (2) drives the planet carrier (18) to rotate, so that a third gear is realized;
when the first clutch (9), the third clutch (11) and the second brake (14) are combined, the first planet wheel (2) drives the planet carrier (18) and the second sun wheel (8) to rotate, so that fourth gear is realized;
when the second clutch (10) and the second brake (14) are combined, the first planet wheel (2) drives the planet carrier (18) to rotate, and the second gear ring (4) is braked to realize a fifth gear;
when the second clutch (10) and the fourth clutch (12) are combined, the input shaft (15) drives the planet carrier (18) and the second sun gear (8) to rotate, so that a sixth gear is realized;
when the fourth clutch (12) and the first brake (13) are combined, the input shaft (15) drives the second sun gear (8) to rotate, and the planet carrier (18) is braked to realize a seventh gear;
when the second clutch (10), the third clutch (11) and the second brake (14) are combined, the input shaft (15) drives the planet carrier (18) to rotate, and the second gear ring (4) is braked, so that eighth gear is realized.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710442155.4A CN107120396B (en) | 2017-06-13 | 2017-06-13 | Three-stage planetary gear train automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710442155.4A CN107120396B (en) | 2017-06-13 | 2017-06-13 | Three-stage planetary gear train automatic transmission |
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| Publication Number | Publication Date |
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| CN107120396A CN107120396A (en) | 2017-09-01 |
| CN107120396B true CN107120396B (en) | 2023-08-08 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201710442155.4A Active CN107120396B (en) | 2017-06-13 | 2017-06-13 | Three-stage planetary gear train automatic transmission |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108843753A (en) * | 2018-08-21 | 2018-11-20 | 盛瑞传动股份有限公司 | Multiple-speed gear-box |
| EP4075021B1 (en) * | 2021-04-16 | 2023-10-18 | Volvo Construction Equipment AB | A transmission arrangement |
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| US8961357B2 (en) * | 2012-12-04 | 2015-02-24 | Ford Global Technologies, Llc | Multi-speed automatic transmission |
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| DE102004041509A1 (en) * | 2004-08-27 | 2006-03-16 | Zf Friedrichshafen Ag | Automobile multi-speed gearbox, with eight forward and two reverse gears, has three planet wheel sets and six switch units between the drive input and output shafts |
| CN101970903A (en) * | 2008-02-28 | 2011-02-09 | Zf腓德烈斯哈芬股份公司 | Multi-stage gearbox |
| CN102094943A (en) * | 2009-12-03 | 2011-06-15 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission having three planetary gear sets |
| CN102434638A (en) * | 2010-09-13 | 2012-05-02 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission having stacked planetary gear sets |
| CN102588528A (en) * | 2011-01-05 | 2012-07-18 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission having stacked planetary gear sets |
| CN103511563A (en) * | 2013-10-22 | 2014-01-15 | 徐攀 | Dual-planetary-gear-train continuously variable transmission mechanism |
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| CN206918176U (en) * | 2017-06-13 | 2018-01-23 | 中南林业科技大学 | Third-level planetary train automatic transmission |
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| CN107120396A (en) | 2017-09-01 |
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