A six-speed powertrain of an automatic transmission includes a first single pinion planetary gear set having a first sun gear, two a first planet carriers carrier, a first planetary gear, and a first ring gear. A second single pinion planetary gear set has a second sun gear, a second planetary gear, and a second ring gear. A double pinion planetary gear set has a third sun gear, a pair of third planetary gears, and a third ring gear. One planetary gear of the pair of third planetary gears and the second planetary gear are commonly connected by a common planet carrier such that the second and third planetary gears may independently rotate.
|
0. 32. A powertrain of an automatic transmission comprising first, second, and third planetary gear sets, an input shaft, and a transmission case, wherein:
the first planetary gear set is a first single pinion planetary gear set, the second planetary gear set is a second single pinion planetary gear set, and the third planetary gear set is a double pinion planetary gear set;
the first single pinion planetary gear set has a first sun gear, a first planet carrier, a first planetary gear, and a first ring gear;
the second single pinion planetary gear set has a second sun gear, a second planetary gear, and a second ring gear;
the double pinion planetary gear set is disposed adjacent to the second single pinion planetary gear set and has a third sun gear, a pair of third planetary gears, and a third ring gear;
one planetary gear of the pair of third planetary gears and the second planetary gear are commonly connected by a common planet carrier such that the second and third planetary gears may independently rotate;
the third ring gear and the first ring gear are fixedly connected such that they are integrally formed;
the second ring gear and the first planet carrier are fixedly connected; and
a torque of the input shaft is always transmitted to the second sun gear or the third sun gear.
1. A six-speed powertrain of an automatic transmission comprising first, second, and third planetary gear sets, an input shaft, and a transmission case, wherein:
the first planetary gear set is a first single pinion planetary gear set, the second planetary gear set is a second single pinion planetary gear set, and the third planetary gear set is a double pinion planetary gear set;
the first single pinion planetary gear set has a first sun gear, two a first planet carriers carrier, a first planetary gear, and a first ring gear;
the second single pinion planetary gear set has a second sun gear, a second planetary gear, and a second ring gear;
the double pinion planetary gear set is disposed adjacent to the second single pinion planetary gear set and has a third sun gear, a pair of third planetary gears, and a third ring gear;
one planetary gear of the pair of third planetary gears and the second planetary gear are commonly connected by a common planet carrier such that the second and third planetary gears may independently rotate;
the third ring gear and the first ring gear are fixedly connected such that they are integrally formed;
the second ring gear and one the first planet carrier are fixedly connected; and
a torque of the input shaft is always transmitted to the second sun gear or the third sun gear.
16. A six-speed powertrain of an automatic transmission comprising first, second, and third planetary gear sets, an input shaft, and a transmission case, wherein:
the first planetary gear set is a first single pinion planetary gear set, the second planetary gear set is a second single pinion planetary gear set, and the third planetary gear set is a double pinion planetary gear set;
the first single pinion planetary gear set has a first sun gear, two a first planet carriers carrier, a first planetary gear, and a first ring gear;
the second single pinion planetary gear set has a second sun gear, a second planetary gear, and a second ring gear;
the double pinion planetary gear set is disposed adjacent to the second planetary gear set and has a third sun gear, a pair of third planetary gears, and a third ring gear;
one planetary gear of the pair of third planetary gears and the second planetary gear are commonly connected by a common planet carrier such that the second and third planetary gears may independently rotate;
the third ring gear and the first ring gear are fixedly connected such that they are integrally formed;
the second ring gear and one the first planet carrier are fixedly connected;
a torque of the input shaft is always transmitted to the third sun gear or the second sun gear; and
frictional elements consisting of two clutches and three brakes are operated to realize six forward speeds and one reverse speed.
2. The powertrain of
the first sun gear is variably connected with the input shaft via a clutch;
the one first planet carrier and the second ring gear are variably connected with the input shaft via a clutch;
the other first planet carrier is variably connected with the transmission case via a brake and a one-way clutch disposed in parallel;
the third sun gear is variably connected with the transmission case via a brake;
the first sun gear is variably connected with the transmission case via a brake;
the second sun gear is fixedly connected with the input shaft; and
the third ring gear is fixedly connected with the first ring gear and they act as output elements.
3. The powertrain of
4. The powertrain of
5. The powertrain of
a second planet carrier is additionally included in the second single pinion planetary gear set and is variably connected with the input shaft via a clutch;
the other first planet carrier is variably connected with the transmission case via a brake and a one way one-way clutch disposed in parallel;
the third sun gear is variably connected with the transmission case via a brake;
the first sun gear is variably connected with the transmission case via a brake;
the second sun gear is fixedly connected with the input shaft; and
the third ring gear is fixedly connected with the first ring gear and they act as output elements.
6. The powertrain of
7. The powertrain of
8. The powertrain of
the first sun gear is variably connected with the input shaft via a clutch;
the common planet carrier commonly connecting the second single pinion planatery planetary gear set and the double pinion planetary gear set is variably connected with the input shaft via a clutch;
the other first planet carrier is variably connected with the transmission case via a brake and a one-way clutch disposed in parallel;
the third sun gear is variably connected with the transmission case via a brake;
the first sun gear is variably connected with the transmission case via a brake;
the second sun gear is fixedly connected with the input shaft; and
the third ring gear is fixedly connected with the first ring gear and they act as output elements.
9. The powertrain of
10. The powertrain of
11. The powertrain of
the second sun gear is variably connected with the input shaft via a clutch;
a third planet carrier is additionally included in the double pinion planetary gear set and is variably connected with the input shaft via a clutch;
the third planet carrier is variably connected with the transmission case via a brake and an a one-way clutch disposed in parallel;
the first sun gear is variably connected with the transmission case via a brake;
the second sun gear is variably connected with the transmission case via a brake;
the third sun gear is fixedly connected with the input shaft; and
the other first planet carrier acts as an output element.
12. The powertrain of
the second sun gear is variably connected with the input shaft via a clutch;
the common planet carrier is variably connected with the input shaft via a clutch;
a third planet carrier is additionally included in the double pinion planetary gear set and is variably connected with the transmission case via a brake and an one way a one-way clutch disposed in parallel;
the first sun gear is variably connected with the transmission case via a brake;
the second sun gear is variably connected with the transmission case via a brake;
the third sun gear is fixedly connected with the input shaft; and
the other first planet carrier acts as an output element.
13. The powertrain of
the second sun gear is variably connected with the input shaft via a clutch;
a third planet carrier is additionally included in the double pinion planetary gear set and is variably connected with the input shaft via a clutch;
a second planet carrier is additionally included in the second single pinion planetary gear set, separately formed from the second planetary gear, and is variably connected with the transmission case via a brake and an one way a one-way clutch disposed in parallel;
the first sun gear is variably connected with the transmission case via a brake;
the second sun gear is variably connected with the transmission case via a brake;
the third sun gear is fixedly connected with the input shaft; and
the other first planet carrier acts as an output element.
14. The powertrain of
the second sun gear is variably connected with the input shaft via a clutch;
the third ring gear is variably connected with the input shaft via a clutch;
a second planet carrier is additionally included in the second single pinion planetary gear set, separately formed from the second planetary gear, and is variably connected with the transmission case via a brake and an one way a one-way clutch disposed in parallel;
the first sun gear is variably connected with the transmission case via a brake;
the second sun gear is variably connected with the transmission case via a brake;
the third sun gear is fixedly connected with the input shaft; and
the other first planet carrier acts as an output element.
15. The powertrain of any one of
17. The powertrain of
the first sun gear is variably connected with the input shaft via a first clutch;
the one first planet carrier and the second ring gear are variably connected with the input shaft via a second clutch;
the other first planet carrier is variably connected with the transmission case via a first brake and a one-way clutch disposed in parallel;
the third sun gear is variably connected with the transmission case via a second brake;
the first sun gear is variably connected with the transmission case via a third brake;
the second sun gear is fixedly connected with the input shaft; and
the third ring gear is fixedly connected with the first ring gear and they act as output elements.
18. The powertrain of
19. The powertrain of
20. The powertrain of
the first sun gear is variably connected with the input shaft via a first clutch;
a second planet carrier is additionally included in the second single pinion planetary gear set and is variably connected with the input shaft via a second clutch;
the other first planet carrier is variably connected with the transmission case via a first brake and a one way one-way clutch disposed in parallel;
the third sun gear is variably connected with the transmission case via a second brake;
the first sun gear is variably connected with the transmission case via a third brake;
the second sun gear is fixedly connected with the input shaft; and
the third ring gear is fixedly connected with the first ring gear and they act as output elements.
21. The powertrain of
the third ring gear is connected with the output gear and acts as an output element.
22. The powertrain of
the first ring gear is connected with the output gear and acts as an output element.
23. The powertrain of
the common planet carrier is variably connected with the input shaft via a second clutch;
the other first planet carrier is variably connected with the transmission case via a first brake and a one-way clutch disposed in parallel;
the third sun gear is variably connected with the transmission case via a second brake;
the first sun gear is variably connected with the transmission case via a third brake;
the second sun gear is fixedly connected with the input shaft; and
the third ring gear is fixedly connected with the first ring gear and they act as output elements.
24. The powertrain of
the third ring gear is connected with the output gear and acts as an output element.
25. The powertrain of
the first ring gear is connected with the output gear and acts as an output element.
26. The powertrain of
the second sun gear is variably connected with the input shaft via a first clutch;
a third planet carrier is additionally included in the double pinion planetary gear set and is variably connected with the input shaft via a second clutch;
the third planet carrier is also variably connected with the transmission case via a first brake and an a one-way clutch disposed in parallel;
the first sun gear is variably connected with the transmission case via a second brake;
the second sun gear is variably connected with the transmission case via a third brake;
the third sun gear is fixedly connected with the input shaft; and
the other first planet carrier acts as an output element.
27. The powertrain of
the second sun gear is variably connected with the input shaft via a first clutch;
the common planet carrier being commonly connected with the second single pinion planetary gear set and the double pinion planetary gear set is variably connected with the input shaft via a second clutch;
a third planet carrier is additionally included in the double pinion planetary gear set and is variably connected with the transmission case via a first brake and an one way a one-way clutch disposed in parallel;
the first sun gear is variably connected with the transmission case via a second brake;
the second sun gear is variably connected with the transmission case via a third brake;
the third sun gear is fixedly connected with the input shaft; and
the other first planet carrier acts as an output element.
28. The powertrain of
the second sun gear is variably connected with the input shaft via a first clutch;
a third planet carrier is additionally included in the double pinion planetary gear set and is variably connected with the input shaft via a second clutch;
a second planet carrier is additionally included in the second single pinion planetary gear set, separately formed from the second planetary gear, and is variably connected with the transmission case via a first brake and an one way a one-way clutch disposed in parallel;
the first sun gear is variably connected with the transmission case via a second brake;
the second sun gear is variably connected with the transmission case via a third brake;
the third sun gear is fixedly connected with the input shaft; and
the other first planet carrier acts as an output element.
29. The powertrain of
the second sun gear is variably connected with the input shaft via a first clutch;
the third ring gear is variably connected with the input shaft via a second clutch;
a second planet carrier is additionally included in the second single pinion planetary gear set, separately formed from the second planetary gear, and is variably connected with the transmission case via a first brake and an one way a one-way clutch disposed in parallel;
the first sun gear is variably connected with the transmission case via a second brake;
the second sun gear is variably connected with the transmission case via a third brake;
the third sun gear is fixedly connected with the input shaft; and
the other first planet carrier acts as an output element.
30. The powertrain of any one of
the first planet carrier acting as an output element is connected with an output gear.
31. The powertrain of any one of
the second brake and the one-way clutch are operated for a first forward speed;
the one-way clutch is released and the third brake is operated for a second forward speed from the first forward speed;
the third brake is released and the first clutch is operated for a third forward speed from the second forward speed;
the first clutch is released and the second clutch is operated for a fourth forward speed from the third forward speed;
the second brake is released and the first clutch is operated for a fifth forward speed from the fourth forward speed;
the first clutch is released and the third brake is operated for a sixth forward speed from the fifth forward speed; and
the first clutch and the first brake are operated for a reverse speed.
|
|||||||||||||||||||||||
This application claims priority to and the benefit of Korean Patent Application No. 10-2004-0090878 filed in the Korean Intellectual Property Office on Nov. 9, 2004, the entire contents of which are incorporated herein by reference.
(a) Field of the Invention
The present invention relates to a six-speed powertrain of an automatic transmission of a vehicle installed in an automatic transmission and realizing six forward speeds and one reverse speed.
(b) Description of the Related Art
A multi-stage gearshift mechanism of an automatic transmission includes a plurality of planetary gear sets. A powertrain having such a plurality of planetary gears sets varies the torque in multi-stages and outputs it to an output shaft when receiving a converted engine torque from a torque converter.
The more speeds the powertrain of an automatic transmission has, the better the power performance and fuel consumption are. Therefore, it is desirable for powertrains to have as many speeds as possible.
Even for the same number of speeds, durability, power transmission efficiency, and size/weight of a transmission are substantially dependent on how planetary gear sets are arranged. Therefore, research for more structural strength, less power loss, and more compact packaging are continuously being conducted.
Usually, development of a powertrain using planetary gear sets does not devise a wholly new type of planetary gear set. To the contrary, it invokes how single/double pinion planetary gear sets are combined, and how clutches, brakes, and one-way clutches are disposed to the combination of Ravingneaux planetary gear sets such that required shift speeds and speed ratios are realized with minimal power loss.
For a manual transmission, too many speeds cause a driver the inconvenience of excessive manual shifting. However, for an automatic transmission, a transmission control unit automatically executes shifting by controlling the operation of the powertrain, and therefore, more speeds usually implies more merits.
Accordingly, research of four-speed and five-speed powertrains has been undertaken, and recently, a powertrain of an automatic transmission enabling six forward speeds and one reverse speed has been developed. However, current six-speed transmissions have a number of drawbacks including excessive size and weight and low durability.
The above information disclosed in this Background section is only for enhancement of understanding of the background of the invention and therefore it may contain information that does not form the prior art that is already known in this country to a person of ordinary skill in the art.
Embodiments of the present invention to provide a six-speed powertrain of an automatic transmission having advantages of minimizing a length and weight of the transmission. Therefore, according to the present invention, one planetary gear of a double pinion planetary gear set and a planetary gear of a single pinion planetary gear set are rotatably supported by one common planet carrier, and at least two ring gears are integrally formed, such that an axial supporting structure is excluded.
An exemplary six-speed powertrain of an automatic transmission according to an embodiment of the present invention includes first, second, and third planetary gear sets, an input shaft, and a transmission case, wherein a first single pinion planetary gear set has a first sun gear, twothethetwotwotwotwo a first planet carriers PC1 rotatably supporting a first planetary gear P1 (engaged with both the first sun gear S1 and the first ring gear R1) at both sides of the first planetary gear P1.
The double pinion planetary gear set DPG includes a third sun gear S3, a third ring gear R3, and a pair of third planetary gears P3 engaged with the third sun gear S3 and the third ring gear R3. One of the pair of third planetary gears P3 is connected with a second planetary gear P2 of the second single pinion planetary gear set SPG2 via a common planet carrier CPC such that the third planetary gear P3 and the second planetary gear P2 rotate independently from each other.
In addition, in the second single pinion planetary gear set SPG2, the second planetary gear P2 (engaged with both a second sun gear S2 and a second ring gear R2) is rotatably carried by a second planet carrier PC2 as well as by the common planet carrier CPC (connected with one of the third pinion planetary gears P3 of the double pinion planetary gear set DPG).
Here, the arrangement and operation of the five frictional elements is the same as in the first exemplary embodiment of the present invention where the third ring gear R3 of the double pinion planetary gear set DPG and the first ring gear R1 of the first single pinion planetary gear set SPG1 are directly and fixedly connected with each other.
In addition, the second ring gear R2 of the second single pinion planetary gear set SPG2 is fixedly connected with the corresponding first planet carrier PC1 of the first single pinion planetary gear set SPG1 as in the first exemplary embodiment of the present invention.
However, according to the first exemplary embodiment of the present invention, the second sun gear S2 of the second single pinion planetary gear set SPG2 is fixedly connected to the input shaft 3, and the first sun gear S1 of the first single pinion planetary gear set SPG1 is variably connected to the input shaft 3 via the first clutch C1. On the other hand, according to the tenth exemplary embodiment of the present invention, the third sun gear S3 of the double pinion planetary gear set DPG is fixedly connected to the input shaft 3 and the second sun gear S2 is variably connected with the input shaft 3 via the first clutch C1 and acts as a variable input element, and is variably connected with the transmission case 1 via the third brake B3 and acts as a variable fixed element.
According to this exemplary embodiment of the present invention, the first sun gear S1 of the first single pinion planetary gear set SPG1 is connected with the transmission case with a second brake B2, and acts as a variable fixed element, unlike in the first exemplary embodiment of the present invention.
In addition, the second planet carrier PC2 is variably connected to the transmission case 1 via a first brake B1 and an one way a one-way clutch OWC (which are disposed in parallel) and acts as a variable fixed element, and the third ring gear R3 is variably connected to the input shaft 3 via a second clutch C2 and acts as a variable input element, unlike in the first exemplary embodiment.
In addition, according to the tenth exemplary embodiment of the present invention, the other first planet carrier PC1 (not the one fixedly connected with the second ring gear R2) is connected with an output gear OUT_GEAR and acts as an output element, unlike in the first exemplary embodiment of the present invention where the third ring gear R3 is connected with the output gear OUT_GEAR such that the third ring gear R3 and the first ring gear R1 act as output elements.
According to the tenth exemplary embodiment of the present invention, in the power delivery paths from the input shaft 3 to the first and second single pinion planetary gear sets SPG1 and SPG2 and the double pinion planetary gear set DPG using five frictional elements the power is delivered from the input shaft 3 to the third sun gear S3, the second sun gear S2 and the third planet carrier PC3 act as variable input elements, and the first sun gear S1, the second sun gear S2, and the third planet carrier PC3 act as variable fixed elements, unlike in the first exemplary embodiment of the present invention. The shifting process for realizing six forward speeds and one reverse speed may be explained referring to the three speed lines as shown in FIG. 18 and FIG. 19. However, the operational chart as shown in
FIG. 18 and
Since analyzing the above-mentioned speed lines about respective planetary gear sets is obvious for a person of an ordinary skill in the art, except for the description regarding the first exemplary embodiment of the present invention, a detailed description about the second to tenth exemplary embodiments of the present invention has been omitted.
While this invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.
As described above, the powertrain according to the present invention includes first and second single pinion planetary gear sets and a double pinion planetary gear set. One planetary gear of the double pinion planetary gear set and one planetary gear of the second single pinion planetary gear set are connected with each other so as to rotate independently, and at least two ring gears are connected as an integral form, such that an axial supporting structure is excluded, and the length and weight of the transmission can be minimized.
In addition, since an output gear (OUT_GEAR) is connected with a ring gear (or with a planet carrier fixedly connected with a ring gear) operational torque can be stabilized and durability of the planet carrier can be improved.
While this invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.
Shim, Hyu Tae, Seo, Kang Soo, Soh, Byeong Ho, Lim, Ki Been
| Patent | Priority | Assignee | Title |
| 8858376, | Jan 12 2011 | GM Global Technology Operations, LLC | Hybrid powertrain for a motor vehicle |
| Patent | Priority | Assignee | Title |
| 5030186, | Feb 03 1989 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission |
| 6824492, | Oct 18 2001 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission |
| 7048669, | Oct 18 2001 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission |
| 7377873, | Dec 22 2004 | Hyundai Motor Company | Six-speed powertrain of an automatic transmission |
| 20030119623, | |||
| 20060135309, | |||
| DE19912480, | |||
| EP1265006, | |||
| JP2003130149, |
| Executed on | Assignor | Assignee | Conveyance | Frame | Reel | Doc |
| Mar 12 2009 | Hyundai Motor Company | (assignment on the face of the patent) | / |
| Date | Maintenance Fee Events |
| Apr 18 2011 | M1551: Payment of Maintenance Fee, 4th Year, Large Entity. |
| Dec 05 2011 | ASPN: Payor Number Assigned. |
| Apr 30 2015 | M1552: Payment of Maintenance Fee, 8th Year, Large Entity. |
| Apr 23 2019 | M1553: Payment of Maintenance Fee, 12th Year, Large Entity. |
| Date | Maintenance Schedule |
| Nov 16 2013 | 4 years fee payment window open |
| May 16 2014 | 6 months grace period start (w surcharge) |
| Nov 16 2014 | patent expiry (for year 4) |
| Nov 16 2016 | 2 years to revive unintentionally abandoned end. (for year 4) |
| Nov 16 2017 | 8 years fee payment window open |
| May 16 2018 | 6 months grace period start (w surcharge) |
| Nov 16 2018 | patent expiry (for year 8) |
| Nov 16 2020 | 2 years to revive unintentionally abandoned end. (for year 8) |
| Nov 16 2021 | 12 years fee payment window open |
| May 16 2022 | 6 months grace period start (w surcharge) |
| Nov 16 2022 | patent expiry (for year 12) |
| Nov 16 2024 | 2 years to revive unintentionally abandoned end. (for year 12) |