KR101836824B1 - Automatic transmission for vehicle - Google Patents
Automatic transmission for vehicle Download PDFInfo
- Publication number
- KR101836824B1 KR101836824B1 KR1020160021240A KR20160021240A KR101836824B1 KR 101836824 B1 KR101836824 B1 KR 101836824B1 KR 1020160021240 A KR1020160021240 A KR 1020160021240A KR 20160021240 A KR20160021240 A KR 20160021240A KR 101836824 B1 KR101836824 B1 KR 101836824B1
- Authority
- KR
- South Korea
- Prior art keywords
- clutch
- planetary gear
- gear set
- brake
- selectively connected
- Prior art date
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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
- F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten 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
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse 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
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
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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
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The present invention relates to an automatic transmission for a vehicle, and more particularly, to an automatic transmission for a vehicle, which comprises an input shaft receiving power from an engine, a first planetary gear set for inputting power from the input shaft, An output shaft connected to the complex planetary gear set for outputting the shifted power, four clutches selectively transmitting the power to the first planetary gear set and the complex planetary gear set, a first planetary gear set, And three brakes selectively connecting the gear set to the transmission housing to implement the forward tenth and reverse one-speed gear stages.
Description
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automatic transmission for a vehicle, and more particularly, to an automatic transmission for a vehicle that uses two planetary gear sets, four clutches, and three brakes to implement a forward 10-speed reverse 1-speed shift stage.
Generally, an automatic transmission is implemented by a combination of a plurality of planetary gear sets, and functions to transmit rotational power transmitted from a torque converter to a multi-stage automatic transmission and transmit it to an output shaft.
The automatic transmissions have been designed to realize more efficient transmission speeds as more transmission speeds can be implemented, as well as to provide vehicles with superior power performance and fuel economy.
The automatic transmission has different operating mechanisms depending on the connection configuration of the rotating elements (sun gear, planetary carrier, ring gear) even when the same transmission speed is implemented.
On the other hand, the automatic transmission has to realize a plurality of speed change stages, in order to release one friction member and to operate the other friction member in a sequential shift from a shift control viewpoint to a neighboring speed change stage.
BACKGROUND ART [0002] The background art of the present invention is disclosed in Korean Patent Laid-Open Publication No. 2008-0033789 (published on Apr. 14, 2008, entitled " Gear Train of 9-speed Automotive Transmission).
An object of the present invention is to provide an automatic transmission for a vehicle that implements a forward 10-speed reverse 1-speed gear position using two planetary gear sets, four clutches, and three brakes.
An automatic transmission for a vehicle according to the present invention comprises: an input shaft receiving power of an engine; A first planetary gear set to which power is input from the input shaft; A complex planetary gear set in which power is selectively transmitted from the input shaft and the first planetary gear set; An output shaft connected to the complex planetary gear set and outputting shifted power; Four clutches selectively connected to the first planetary gear set and the multiple planetary gear set to transmit power; And three brakes selectively connecting the first planetary gear set and the second planetary gear set to the transmission housing.
A vehicular automatic transmission according to the present invention includes: a first planetary gear set connected to an input shaft; And a second clutch that is selectively connected to the first planetary gear set via second and third clutches and is selectively connected to the input shaft via first and fourth clutches and is connected to the transmission housing via first, And a combined planetary gear set that is selectively connected to the output shaft and transmits the shifted power to the output shaft, the complex planetary gear set including a second planetary gear set and a third planetary gear set, The first planetary gear set and the second planetary gear set are single pinions, and the third planetary gear set is a double pinion.
The first planetary gear set includes a first sun gear coupled to the input shaft; A first ring gear; And a second planetary gear set disposed between the first sun gear and the first ring gear and selectively connected to the third planetary gear set via the second clutch, And a second carrier to which the first carrier is connected.
The second planetary gear set includes a second sun gear selectively connected to the first carrier via the third clutch and selectively connected to the transmission housing through the first brake; A 23rd ring gear connected to the output shaft; And a 23rd carrier disposed between the second sun gear and the 23rd ring gear and connected to the second planetary gear set and selectively connected to the transmission housing via the second brake, .
The third planetary gear set being selectively connected to the input shaft via the fourth clutch and selectively connected to the transmission housing via the third brake; And a third ring gear which is disposed between the third sun gear and the ring gear and is connected to the 23rd carrier and is selectively connected to the first carrier via the second clutch, And a third carrier selectively connected to the input shaft.
Wherein the multi-speed change stage includes a reverse shift stage in which the second brake and the third clutch are implemented simultaneously; A forward first speed change stage in which the third brake and the third clutch are implemented simultaneously; A forward second speed change stage in which the third brake and the second clutch are implemented by being operated simultaneously; A forward third speed change stage in which the second clutch and the third clutch are implemented by being operated simultaneously; A forward 4th-speed shift stage in which the first brake and the second clutch are implemented simultaneously; A forward fifth-speed change-speed stage in which the second clutch and the fourth clutch are implemented simultaneously; A forward 6-speed shift stage in which the first brake and the fourth clutch are implemented simultaneously; A forward 7th-speed shift stage in which the third clutch and the fourth clutch are implemented simultaneously; An advancing eighth speed change stage in which the first clutch and the fourth clutch are implemented simultaneously; A forward Ninth speed-change stage in which the first clutch and the third clutch are implemented simultaneously; And a forward 10th speed gear stage in which the first brake and the first clutch are implemented by being operated simultaneously.
The automatic transmission for a vehicle according to the present invention can realize forward 10th speed and reverse 1 speed gear steps using one planetary gear set, one compound planetary gear set, four clutches, and three brakes.
1 is a block diagram schematically showing an automatic transmission for a vehicle according to an embodiment of the present invention.
2 is an operation table for each gear position of an automatic transmission for a vehicle according to an embodiment of the present invention.
3 is a lever analysis view of an automatic transmission for a vehicle according to an embodiment of the present invention.
Hereinafter, an embodiment of an automatic transmission for a vehicle according to the present invention will be described with reference to the accompanying drawings. In this process, the thicknesses of the lines and the sizes of the components shown in the drawings may be exaggerated for clarity and convenience of explanation. In addition, the terms described below are terms defined in consideration of the functions of the present invention, which may vary depending on the intention or custom of the user, the operator. Therefore, definitions of these terms should be made based on the contents throughout this specification.
FIG. 1 is a configuration diagram schematically showing an automatic transmission for a vehicle according to an embodiment of the present invention. FIG. 2 is an operation table for each gear range of an automatic transmission for a vehicle according to an embodiment of the present invention. Fig. 7 is a lever analysis diagram of an automatic transmission according to an embodiment of the present invention. Fig. 1 to 3, an automatic transmission 1 for a vehicle according to an embodiment of the present invention includes an input shaft IS, a first planetary gear set PG1, a combined planetary gear set CPG, OS, four clutches CL1, CL2, CL3, and CL4, and three brakes B1, B2, and B3. Thus, the power input from the input shaft IS is shifted by the complementary operation of the first planetary gear set PG1 and the second planetary gear set CPG, and then output through the output shaft OS.
The input shaft IS is an input member, and the rotational power to which the torque conversion is performed is inputted through the torque converter input from the crankshaft of the engine. The output shaft OS, as an output member, transmits a driving force to drive the drive wheels through the differential device.
The first planetary gear set PG1 is connected to the input shaft IS and receives power from the input shaft IS.
The compound planetary gear set CPG is selectively transmitted with power from the input shaft IS and the first planetary gear set PG1. The complex planetary gear set (CPG) shifts the input power and provides it to the output shaft OS. The complex planetary gear set CPG is formed by integrating the second planetary gear set PG2 and the third planetary gear set PG3. As an example, a compound planetary gear set (CPG) may be a planetary gear system of a rake type.
The first planetary gear set PG1 and the multiple planetary gear set CPG are selectively connected by the first, second, third and fourth clutches CL1, CL2, CL3 and CL4 to transmit power. The compound planetary gear set CPG is selectively connected to the transmission housing H by the first, second and third brakes B1, B2 and B3.
A single pinion is used for the first and second planetary gear sets PG1 and PG2, and a double pinion is used for the third planetary gear set PG3.
The first planetary gearset PG1 according to the embodiment of the present invention includes a first sun gear S1, a first ring gear R1, and a first planetary gear set PG1 between the first sun gear S1 and the first ring gear R1 And includes a first carrier (C1) that is engaged.
The first sun gear S1 remains connected to the input shaft IS. The first carrier C1 is selectively connected to the third planetary gear set PG3 via the second clutch CL2 and selectively connected to the second planetary gear set PG2 via the third clutch CL3 . A single pinion is used as the first carrier C1.
The second planetary gearset PG2 according to the embodiment of the present invention is provided with the second sun gear S2, the 23rd ring gear R23, the second sun gear S2 and the 23rd ring gear R23 And a 23rd-order carrier C23 that is engaged.
The second sun gear S2 is selectively connected to the first carrier C1 via the third clutch CL3 and selectively connected to the transmission housing H via the first brake B1.
The twenty-third ring gear R23 is connected to the output shaft OS to transmit the shifted power to the output shaft OS. The second planetary gear set PG2 and the third planetary gear set PG3 may share one seventeenth ring gear R23.
The twenty-third carrier C23 is connected to the third planetary gear set PG3 and selectively connected to the transmission housing H via the second brake B2.
The third planetary gear set PG3 according to an embodiment of the present invention includes a third sun gear S3 and a third carrier C3 connected to the 23rd carrier C23.
The third sun gear S3 is selectively connected to the input shaft IS through the fourth clutch CL4 and selectively connected to the transmission housing H via the third brake B3.
The third carrier C3 remains connected to the 23rd carrier C23, and the third planetary gear set PG3 becomes a double pinion. The third carrier C3 is selectively connected to the input shaft IS via the first clutch CL1 and selectively connected to the first carrier C1 via the second clutch CL2.
The automatic transmission 1 for a vehicle according to an embodiment of the present invention includes first, second and third brakes B1, B2 and B3 at respective gear positions and first, second, third and fourth clutches CL1, CL2, CL3, and CL4 are selectively operated.
And the reverse shift stage is realized by simultaneously operating the second brake B2 and the third clutch CL3. The forward first speed gear position is implemented by simultaneously operating the third brake B3 and the third clutch CL3. And the forward second-speed range is implemented by simultaneously operating the third brake B3 and the second clutch CL2. And the forward third speed change stage is implemented by operating the second and third clutches CL2 and CL3 simultaneously. The forward fourth-speed gear position is realized by simultaneously operating the first brake B1 and the second clutch CL2. And the forward fifth-speed gear position is implemented by operating the second and fourth clutches CL2 and CL4 simultaneously. The forward sixth-speed gear position is implemented by simultaneously operating the first brake B1 and the fourth clutch CL4. And the forward seventh speed change stage is realized by simultaneously operating the third and fourth clutches CL3 and CL4. The forward 8th-speed gear position is realized by simultaneously operating the first and fourth clutches CL1 and CL4. The forward 9th-speed gear position is implemented by simultaneously operating the first and third clutches CL1 and CL3. The forward 10th-speed gear position is implemented by simultaneously operating the first brake B1 and the first clutch CL1.
The automatic transmission 1 for a vehicle according to an embodiment of the present invention includes a first planetary gear set PG1, a combined planetary gear set CPG, four clutches CL1, CL2, CL3, CL4, Combining the three brakes (B1, B2, B3), it is possible to implement the forward 10th gear and the reverse 1st gear.
While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it will be understood by those of ordinary skill in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims. I will understand. Accordingly, the true scope of protection of the present invention should be defined by the following claims.
CPG: Complex planetary gear set
PG1, PG2, PG3: First, second and third planetary gear sets
S1, S2, S3: first, second, and third sun gears
C1: first carrier C23: 23rd carrier C3: third carrier
R1: 1st ring gear R23: 23rd ring gear
IS: Input axis OS: Output axis
H: Transmission housing
CL1, CL2, CL3, CL4: First, second, third and fourth clutches
B1, B2, B3: first, second and third brakes
Claims (6)
Second, and third brakes, selectively connected to the first planetary gear set via first, second, and third clutches, and selectively coupled to the input shaft via first and fourth clutches, And a complex planetary gear set that is selectively connected and transmits the shifted power to the output shaft,
Wherein the compound planetary gear set includes a second planetary gear set and a third planetary gear set, wherein the first planetary gear set and the second planetary gear set are single pinions, and the third planetary gear set is a double pinion,
The first planetary gear set
A first sun gear coupled to the input shaft;
A first ring gear; And
And a second planetary gear set disposed between the first sun gear and the first ring gear and selectively connected to the third planetary gear set via the second clutch and selectively connected to the second planetary gear set via the third clutch A first carrier,
The second planetary gear set
A second sun gear selectively connected to the first carrier via the third clutch and selectively connected to the transmission housing through the first brake;
A 23rd ring gear connected to the output shaft; And
And a 23rd carrier disposed between the second sun gear and the 23rd ring gear and connected to the second planetary gear set and selectively connected to the transmission housing through the second brake,
The third planetary gear set
A third sun gear selectively connected to the input shaft via the fourth clutch and selectively connected to the transmission housing through the third brake; And
And a third clutch, which is disposed between the third sun gear and the twenty-third ring gear and remains connected to the twenty-third carrier, and is selectively connected to the first carrier via the second clutch, And a third carrier selectively coupled to the second carrier,
The multi-
A reverse shift stage in which the second brake and the third clutch are implemented simultaneously;
A forward first speed change stage in which the third brake and the third clutch are implemented simultaneously;
A forward second speed change stage in which the third brake and the second clutch are implemented by being operated simultaneously;
A forward third speed change stage in which the second clutch and the third clutch are implemented by being operated simultaneously;
A forward 4th-speed shift stage in which the first brake and the second clutch are implemented simultaneously;
A forward fifth-speed change-speed stage in which the second clutch and the fourth clutch are implemented simultaneously;
A forward 6-speed shift stage in which the first brake and the fourth clutch are implemented simultaneously;
A forward 7th-speed shift stage in which the third clutch and the fourth clutch are implemented simultaneously;
An advancing eighth speed change stage in which the first clutch and the fourth clutch are implemented simultaneously;
A forward Ninth speed-change stage in which the first clutch and the third clutch are implemented simultaneously; And
And a forward 10th speed gear stage in which the first brake and the first clutch are implemented by being operated simultaneously.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020160021240A KR101836824B1 (en) | 2016-02-23 | 2016-02-23 | Automatic transmission for vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020160021240A KR101836824B1 (en) | 2016-02-23 | 2016-02-23 | Automatic transmission for vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| KR20170099442A KR20170099442A (en) | 2017-09-01 |
| KR101836824B1 true KR101836824B1 (en) | 2018-03-12 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| KR1020160021240A KR101836824B1 (en) | 2016-02-23 | 2016-02-23 | Automatic transmission for vehicle |
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| Country | Link |
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| KR (1) | KR101836824B1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20220016323A (en) * | 2020-07-30 | 2022-02-09 | 현대트랜시스 주식회사 | Automatic transmission for car |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4039309B2 (en) | 2002-05-27 | 2008-01-30 | トヨタ自動車株式会社 | Automatic transmission for vehicles |
-
2016
- 2016-02-23 KR KR1020160021240A patent/KR101836824B1/en active IP Right Grant
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4039309B2 (en) | 2002-05-27 | 2008-01-30 | トヨタ自動車株式会社 | Automatic transmission for vehicles |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20220016323A (en) * | 2020-07-30 | 2022-02-09 | 현대트랜시스 주식회사 | Automatic transmission for car |
| KR102385620B1 (en) * | 2020-07-30 | 2022-04-12 | 현대트랜시스 주식회사 | Automatic transmission for car |
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| Publication number | Publication date |
|---|---|
| KR20170099442A (en) | 2017-09-01 |
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