KR101836825B1 - Automatic transmission for vehicle - Google Patents
Automatic transmission for vehicle Download PDFInfo
- Publication number
- KR101836825B1 KR101836825B1 KR1020160021241A KR20160021241A KR101836825B1 KR 101836825 B1 KR101836825 B1 KR 101836825B1 KR 1020160021241 A KR1020160021241 A KR 1020160021241A KR 20160021241 A KR20160021241 A KR 20160021241A KR 101836825 B1 KR101836825 B1 KR 101836825B1
- Authority
- KR
- South Korea
- Prior art keywords
- planetary gear
- gear set
- clutch
- selectively connected
- clutches
- Prior art date
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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
- 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
- F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing 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
- F16H2200/003—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
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four 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
Landscapes
- 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 having an input shaft receiving power of an engine, a first planetary gear set, a first planetary gear set, a second planetary gear set connected to the input shaft and the transmission housing, A fourth planetary gear set connected to the input shaft and the first planetary gear set to the third planetary gear set, a third planetary gear set connected to the third planetary gear set, An output shaft for outputting the first planetary gear set and the fourth planetary gear set, five clutches selectively connecting the first to fourth planetary gear sets, two brakes for selectively connecting the second planetary gear set and the third planetary gear set to the transmission housing, Speed forward and reverse 1-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 four planetary gear sets, five clutches, and two 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 four forward planetary gear sets, five clutches, and two brakes to implement a forward 10-speed reverse 1-speed gear position.
An automatic transmission for a vehicle according to an embodiment of the present invention includes: an input shaft receiving power of an engine; A first planetary gear set; The first planetary gear set, the input shaft, a second planetary gear set connected to the transmission housing, A third planetary gear set connected to the input shaft, the transmission housing, and the first planetary gear set; A fourth planetary gear set connected to the first planetary gear set to the third planetary gear set; An output shaft connected to the third planetary gear set and outputting shifted power; Five clutches selectively connecting the first planetary gear set to the fourth planetary gear set; And two brakes selectively connecting the second planetary gear set and the third planetary gear set to the transmission housing.
An automatic transmission for a vehicle according to an embodiment of the present invention includes: a first planetary gear set; A second clutch and a third clutch, and a part of which is selectively connected to the first planetary gear set via a fourth clutch while a part of the planetary gear set remains connected to the first planetary gear set, A second planetary gear set selectively connected to the transmission housing via a second brake; Selectively connected to the input shaft via the first clutch and selectively connected with the first planetary gear set via the fifth clutch, and selectively connected to the transmission housing via the first brake, A third planetary gear set; And a fourth planetary gear set that is selectively connected to the input shaft via the first clutch and selectively connected to the first planetary gear set via the fourth clutch, Wherein the first planetary gear set, the third planetary gear set, and the fourth planetary gear set are single pinions, and the second planetary gear set is a double pinion .
The first planetary gear set having a first sun gear retaining a connection with the second planetary gear set; A first ring gear; And a fourth planetary gear set disposed between the first sun gear and the first ring gear and selectively connected to the second planetary gear set and the fourth planetary gear set via the fourth clutch, And a first carrier selectively connected to the planetary gear set.
The second planetary gear set is selectively connected to the input shaft via the third clutch and selectively connected to the transmission housing through the second brake; A second ring gear selectively connected to the first carrier via the fourth clutch, and maintained in a state of being connected to the fourth planetary gear set; And a second carrier disposed between the second sun gear and the second ring gear, the second carrier being selectively connected to the input shaft via the second clutch, the second carrier being connected to the first sun gear and being a double pinion .
The third planetary gear set being selectively connected to the first carrier via the fifth clutch and selectively connected to the transmission housing via the first brake; A third ring gear selectively connected to the input shaft via the first clutch and maintained in a state of being connected to the fourth planetary gear set; And a third carrier which is disposed between the third sun gear and the third ring gear and is connected to the output shaft and maintains a state of being connected to the fourth planetary gear set.
The fourth planetary gear set is selectively connected to the first carrier via the fourth clutch and is maintained in a state of being connected to the second ring gear; A fourth ring gear maintaining a state of being connected to the third carrier; And a fourth carrier disposed between the fourth sun gear and the fourth ring gear, the fourth carrier being selectively connected to the input shaft via the first clutch and maintaining a state of being connected to the third ring gear .
Wherein the multi-stage shift stage includes a reverse shift stage in which the first brake and the third and fourth clutches are implemented simultaneously; A forward first speed change stage in which the first brake and the second and fourth clutches are implemented by being operated simultaneously; A forward second speed change stage in which the first and second brakes and the second clutch are implemented simultaneously; A forward third speed change stage in which the first brake and the second and third clutches are implemented by being operated simultaneously; A fourth forward speed shift stage in which the second, third, and fifth clutches are implemented simultaneously; A forward 5th speed gear stage in which the first, second and fifth clutches are implemented simultaneously; A forward 6th speed gear stage in which the first, second and third clutches are implemented simultaneously; A forward seventh speed change stage in which the second brake and the first and second clutches are implemented simultaneously; A forward eighth speed change stage in which the first, second, and fourth clutches are implemented simultaneously; A forward Ninth speed-change stage in which the second brake and the first and fourth clutches are implemented simultaneously; And a forward 10th speed gear stage in which the first, third and fourth clutches 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 four planetary gear sets, five clutches, and two 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 connection diagram of a planetary gear lever 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. 1 is a connection diagram of a planetary gear lever of an automatic transmission for a vehicle according to an embodiment. 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 second planetary gear set PG2, 3 planetary gear set PG3, a fourth planetary gear set PG4, and an output shaft OS. The power input from the input shaft IS is shifted by the complementary operation of the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4, .
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 second planetary gear set PG2 is connected to the first planetary gear set PG1, the input shaft IS, and the transmission housing H. [ The third planetary gear set PG3 is connected to the first planetary gear set PG1, the input shaft IS, and the transmission housing H. [ The output shaft OS is connected to the third planetary gear set PG3 to output the shifted power. The fourth planetary gear set PG4 is connected to the input shaft IS and the first, second and third planetary gear sets PG1, PG2 and PG3.
A single pinion is used for the first, third and fourth planetary gear sets PG1, PG3 and PG4, and a double pinion is used for the second planetary gear set PG2.
Second, third, fourth and fifth clutches CL1 and CL2 are selectively connected to the first, second, third and fourth planetary gear sets PG1, PG2, PG3 and PG4 and the input shaft IS, First and second brakes B1 and B2 are used so that the transmission housing H and the second and third planetary gear sets PG2 and PG3 are selectively connected to each other. do.
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 second planetary gear set PG2. The first carrier C1 is selectively connected to the second planetary gear set PG2 and the fourth planetary gear set PG4 via the fourth clutch CL4. 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 and the second ring gear R2 and the second planetary gear set PG2 between the second sun gear S2 and the second ring gear R2 And a second carrier C2 that is engaged.
The second sun gear S2 is selectively connected to the input shaft IS via the third clutch CL3 and selectively connected to the transmission housing H via the second brake B2. The second ring gear R2 is selectively connected to the first carrier C1 via the fourth clutch CL4 and remains connected to the fourth planetary gear set PG4. The second carrier C2 is selectively connected to the input shaft IS via the second clutch CL2 and remains connected to the first sun gear S1. A double pinion is used as the second carrier (C2).
The third planetary gear set PG3 according to the embodiment of the present invention is provided with the third sun gear S3, the third ring gear R3, the third sun gear S3 and the third ring gear R3 And a third carrier C3 which is engaged.
The third sun gear S3 is selectively connected to the first carrier C1 via the fifth clutch CL5 and selectively connected to the transmission housing H via the first brake B1. The third ring gear R3 is selectively connected to the input shaft IS via the first clutch CL1 and remains connected to the fourth planetary gear set PG4. The third carrier C3 is connected to the output shaft OS and remains connected to the fourth planetary gear set PG4. A single pinion is used as the third carrier (C3).
The fourth planetary gear set PG4 according to the embodiment of the present invention includes the fourth sun gear S4, the fourth ring gear R4, the fourth sun gear S4 and the fourth ring gear R4 And a fourth carrier C4 which is engaged.
The fourth sun gear S4 is selectively connected to the first carrier C1 via the fourth clutch CL4 and remains connected to the second ring gear R2. And the fourth ring gear R4 remains connected to the third carrier C3. The fourth carrier C4 is selectively connected to the input shaft IS via the first clutch CL1 and remains connected to the third ring gear R3. A single pinion is used as the fourth carrier C4.
The automatic transmission 1 for a vehicle according to the embodiment of the present invention is provided with the first and second brakes B1 and B2 and the first, second, third, fourth and fifth clutches CL1, CL2, CL3, CL4, and CL5 are selectively operated.
The forward speed change stage is realized by the simultaneous operation of the first brake B1 and the third and fourth clutches CL3 and CL4 and the forward first speed range is established by the first brake B1 and the second and fourth clutches CL2 , CL4) are implemented simultaneously. The forward third speed range is implemented by simultaneously operating the first and second brakes B1 and B2 and the second clutch CL2 and the forward third speed range is established by the first brake B1 and the second and third clutches B1 and B2, (CL2, CL3) are implemented simultaneously. CL2 and CL5 are implemented by simultaneously operating the first, second and fifth clutches CL1, CL2 and CL5, and the forward fifth- ) Are implemented simultaneously. The forward sixth speed range is implemented by simultaneously operating the first, second and third clutches CL1, CL2 and CL3. The forward seventh speed range is implemented by the second brake B2 and the first and second clutch CL1 , CL2) are implemented simultaneously. The forward speed is implemented by simultaneously operating the first, second and fourth clutches CL1, CL2 and CL4, and the forward third speed range is implemented by the second brake B2 and the first and fourth clutches CL1 , And CL4 are implemented simultaneously, and the forward 10th-speed gear position is realized by simultaneously operating the first, third, and fourth clutches CL1, CL3, and CL4.
The automatic transmission 1 for a vehicle according to an embodiment of the present invention includes four planetary gear sets, i.e., first, second, third, and fourth planetary gear sets PG1, PG2, PG3, PG4, CL2, CL3, CL4 and CL5 and two brakes, that is, the first and second brakes B1 and B2, And a reverse 1-speed shift stage.
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.
PG1, PG2, PG3, PG4: first, second, third and fourth planetary gear sets
S1, S2, S3, S4: First, second, third, and fourth sun gear
C1, C2, C3, and C4: first, second, third, and fourth carriers
R1, R2, R3, R4: first, second, third, and fourth ring gears
IS: Input axis OS: Output axis
H: Transmission housing
CL1, CL2, CL3, CL4, CL5: First, second, third,
B1, B2: First and second brakes
Claims (7)
A second clutch and a third clutch, and a part of which is selectively connected to the first planetary gear set via a fourth clutch while a part of the planetary gear set remains connected to the first planetary gear set, A second planetary gear set selectively connected to the transmission housing via a second brake;
Selectively connected to the input shaft via the first clutch and selectively connected with the first planetary gear set via the fifth clutch, and selectively connected to the transmission housing via the first brake, A third planetary gear set; And
A fourth planetary gear set selectively connected to the input shaft via the first clutch, selectively connected to the first planetary gear set via the fourth clutch, and maintained in a state of being connected to the third planetary gear set; And a multi-speed change-
Wherein the first planetary gear set, the third planetary gear set, and the fourth planetary gear set are single pinions, and the second planetary gear set is a double pinion.
A first sun gear retaining a state of being connected to the second planetary gear set;
A first ring gear; And
Wherein the first planetary gear set and the fourth planetary gear set are selectively connected to the first planetary gear set and the fourth planetary gear set via the fourth clutch, And a first carrier selectively connected to the gear set.
A second sun gear selectively connected to the input shaft via the third clutch and selectively connected to the transmission housing via the second brake;
A second ring gear selectively connected to the first carrier via the fourth clutch, and maintained in a state of being connected to the fourth planetary gear set; And
And a second carrier disposed between the second sun gear and the second ring gear, the second carrier being selectively connected to the input shaft via the second clutch, the second carrier being connected to the first sun gear and being a double pinion; And the vehicle speed.
A third sun gear selectively connected to the first carrier via the fifth clutch and selectively connected to the transmission housing via the first brake;
A third ring gear selectively connected to the input shaft via the first clutch and maintained in a state of being connected to the fourth planetary gear set; And
And a third carrier which is disposed between the third sun gear and the third ring gear and is connected to the output shaft and maintains a state of being connected to the fourth planetary gear set.
A fourth sun gear selectively connected to the first carrier through the fourth clutch and held in a state of being connected to the second ring gear;
A fourth ring gear maintaining a state of being connected to the third carrier; And
And a fourth carrier which is disposed between the fourth sun gear and the fourth ring gear and is selectively connected to the input shaft through the first clutch and maintains a state of being connected to the third ring gear. The vehicle automatic transmission.
A reverse shift stage in which the first brake and the third and fourth clutches are implemented simultaneously;
A forward first speed change stage in which the first brake and the second and fourth clutches are implemented by being operated simultaneously;
A forward second speed change stage in which the first and second brakes and the second clutch are implemented simultaneously;
A forward third speed change stage in which the first brake and the second and third clutches are implemented by being operated simultaneously;
A fourth forward speed shift stage in which the second, third, and fifth clutches are implemented simultaneously;
A forward 5th speed gear stage in which the first, second and fifth clutches are implemented simultaneously;
A forward 6th speed gear stage in which the first, second and third clutches are implemented simultaneously;
A forward seventh speed change stage in which the second brake and the first and second clutches are implemented simultaneously;
A forward eighth speed change stage in which the first, second, and fourth clutches are implemented simultaneously;
A forward Ninth speed-change stage in which the second brake and the first and fourth clutches are implemented simultaneously; And
And a forward 10th speed gear stage in which the first, third, and fourth clutches are implemented simultaneously.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020160021241A KR101836825B1 (en) | 2016-02-23 | 2016-02-23 | Automatic transmission for vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020160021241A KR101836825B1 (en) | 2016-02-23 | 2016-02-23 | Automatic transmission for vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| KR20170099443A KR20170099443A (en) | 2017-09-01 |
| KR101836825B1 true KR101836825B1 (en) | 2018-03-12 |
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ID=59923647
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| KR1020160021241A KR101836825B1 (en) | 2016-02-23 | 2016-02-23 | Automatic transmission for vehicle |
Country Status (1)
| Country | Link |
|---|---|
| KR (1) | KR101836825B1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101651158B1 (en) * | 2016-07-07 | 2016-08-25 | 에코아이넷 주식회사 | C c t v security system for emergency situation notice based on sound and hybrid cognition, and method for providing thereof |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009197927A (en) * | 2008-02-22 | 2009-09-03 | Kyowa Metal Work Co Ltd | Multistage transmission planetary gear train |
| WO2015108028A1 (en) * | 2014-01-14 | 2015-07-23 | アイシン・エィ・ダブリュ株式会社 | Multi-stage transmission |
-
2016
- 2016-02-23 KR KR1020160021241A patent/KR101836825B1/en active IP Right Grant
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009197927A (en) * | 2008-02-22 | 2009-09-03 | Kyowa Metal Work Co Ltd | Multistage transmission planetary gear train |
| WO2015108028A1 (en) * | 2014-01-14 | 2015-07-23 | アイシン・エィ・ダブリュ株式会社 | Multi-stage transmission |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101651158B1 (en) * | 2016-07-07 | 2016-08-25 | 에코아이넷 주식회사 | C c t v security system for emergency situation notice based on sound and hybrid cognition, and method for providing thereof |
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| Publication number | Publication date |
|---|---|
| KR20170099443A (en) | 2017-09-01 |
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