U.S. patent application number 15/266814 was filed with the patent office on 2017-09-21 for planetary gear train of automatic transmission for vehicle.
This patent application is currently assigned to Hyundai Motor Company. The applicant listed for this patent is Hyundai Motor Company. Invention is credited to Wonmin Cho, Seong Wook Hwang, Wookjin Jang, Seongwook Ji, Jae Chang Kook, Hyun Sik Kwon, Woochurl Son.
Application Number | 20170268625 15/266814 |
Document ID | / |
Family ID | 59855411 |
Filed Date | 2017-09-21 |
United States Patent
Application |
20170268625 |
Kind Code |
A1 |
Kook; Jae Chang ; et
al. |
September 21, 2017 |
PLANETARY GEAR TRAIN OF AUTOMATIC TRANSMISSION FOR VEHICLE
Abstract
A planetary gear train of an automatic transmission for a
vehicle may include an input shaft receiving torque of an engine,
an output shaft outputting torque of the engine, a first planetary
gear set, a second planetary gear set, a third planetary gear set,
a fourth planetary gear set, a first shaft, a second shaft, a third
shaft, a fourth shaft directly connected to the input shaft, a
fifth shaft selectively connectable to the second shaft, a sixth
shaft selectively connectable to the fifth shaft, a seventh shaft
selectively connectable to the fourth shaft and the fifth shaft,
and an eighth shaft directly connected to the output shaft.
Inventors: |
Kook; Jae Chang;
(Hwaseong-si, KR) ; Hwang; Seong Wook; (Gunpo-si,
KR) ; Son; Woochurl; (Seongnam-si, KR) ; Cho;
Wonmin; (Hwaseong-si, KR) ; Kwon; Hyun Sik;
(Seoul, KR) ; Jang; Wookjin; (Yongin-si, KR)
; Ji; Seongwook; (Gunpo-si, KR) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Hyundai Motor Company |
Seoul |
|
KR |
|
|
Assignee: |
Hyundai Motor Company
Seoul
KR
|
Family ID: |
59855411 |
Appl. No.: |
15/266814 |
Filed: |
September 15, 2016 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F16H 2200/2046 20130101;
F16H 3/66 20130101; F16H 2200/0069 20130101; F16H 2200/2012
20130101 |
International
Class: |
F16H 3/66 20060101
F16H003/66 |
Foreign Application Data
Date |
Code |
Application Number |
Mar 18, 2016 |
KR |
10-2016-0032992 |
Claims
1. A planetary gear train of an automatic transmission for a
vehicle comprising: an input shaft receiving torque of an engine;
an output shaft outputting torque of the engine; a first planetary
gear set including a first rotation element, a second rotation
element, and a third rotation element; a second planetary gear set
including a fourth rotation element, a fifth rotation element, and
a sixth rotation element; a third planetary gear set including a
seventh rotation element, an eighth rotation element, and a ninth
rotation element; a fourth planetary gear set including a tenth
rotation element, an eleventh rotation element, and a twelfth
rotation element; a first shaft connecting the first rotation
element to the fourth rotation element; a second shaft connecting
the second rotation element to the eighth rotation element and the
twelfth rotation element; a third shaft connected to the third
rotation element; a fourth shaft connected to the fifth rotation
element and directly connected to the input shaft; a fifth shaft
connected to the sixth rotation element and selectively connectable
to the second shaft; a sixth shaft connected to the seventh
rotation element and selectively connectable to the fifth shaft; a
seventh shaft connecting the ninth rotation element to the tenth
rotation element and selectively connectable to the fourth shaft
and the fifth shaft; and an eighth shaft connected to the eleventh
rotation element and directly connected to the output shaft.
2. The planetary gear train of claim 1, wherein the first shaft and
the third shaft are each selectively connectable to a transmission
housing.
3. The planetary gear train of claim 1, wherein the first rotation
element, the second rotation element, and the third rotation
element comprise a first sun gear, a first planet carrier, and a
first ring gear, the fourth rotation element, the fifth rotation
element, and the sixth rotation element comprise a second sun gear,
a second planet carrier, and a second ring gear, the seventh
rotation element, the eighth rotation element, and the ninth
rotation element comprise a third sun gear, a third planet carrier,
and a third ring gear, and the tenth rotation element, the eleventh
rotation element, and the twelfth rotation element comprise a
fourth sun gear, a fourth planet carrier, and a fourth ring
gear.
4. The planetary gear train of claim 2, further comprising: a first
clutch selectively connecting the fourth shaft to the seventh
shaft; a second clutch selectively connecting the second shaft to
the fifth shaft; a third clutch selectively connecting the fifth
shaft to the seventh shaft; a fourth clutch selectively connecting
the fifth shaft to the sixth shaft; a first brake selectively
connecting the first shaft to the transmission housing; and a
second brake selectively connecting the third shaft to the
transmission housing.
5. A planetary gear train of an automatic transmission for a
vehicle comprising: an input shaft receiving torque of an engine;
an output shaft outputting torque; a first planetary gear set
including a first rotation element, a second rotation element, and
a third rotation element; a second planetary gear set including a
fourth rotation element, a fifth rotation element, and a sixth
rotation element; a third planetary gear set including a seventh
rotation element, an eighth rotation element, and a ninth rotation
element; and a fourth planetary gear set including a tenth rotation
element, an eleventh rotation element, and a twelfth rotation
element, wherein the input shaft is directly connected to the fifth
rotation element, the output shaft is directly connected to the
eleventh rotation element, the first rotation element is directly
connected to the fourth rotation element, the second rotation
element is directly connected to the eighth rotation element and
the twelfth rotation element, the sixth rotation element is
selectively connectable to the second rotation element, the seventh
rotation element is selectively connectable to the sixth rotation
element, the ninth rotation element is selectively connectable to
the fifth rotation element and the sixth rotation element, and the
tenth rotation element is directly connected to the ninth rotation
element and is selectively connectable to the fifth rotation
element.
6. The planetary gear train of claim 5, wherein the first rotation
element and the third rotation element are each selectively
connectable to a transmission housing.
7. The planetary gear train of claim 5, wherein the first rotation
element, the second rotation element, and the third rotation
element comprise a first sun gear, a first planet carrier, and a
first ring gear, the fourth rotation element, the fifth rotation
element, and the sixth rotation element comprise a second sun gear,
a second planet carrier, and a second ring gear, the seventh
rotation element, the eighth rotation element, and the ninth
rotation element comprise a third sun gear, a third planet carrier,
and a third ring gear, and the tenth rotation element, the eleventh
rotation element, and the twelfth rotation element comprise a
fourth sun gear, a fourth planet carrier, and a fourth ring
gear.
8. The planetary gear train of claim 6, further comprising: a first
clutch selectively connecting the fifth rotation element to the
ninth rotation element; a second clutch selectively connecting the
second rotation element to the sixth rotation element; a third
clutch selectively connecting the sixth rotation element to the
ninth rotation element; a fourth clutch selectively connecting the
sixth rotation element to the seventh rotation element; a first
brake selectively connecting the first rotation element to the
transmission housing; and a second brake selectively connecting the
third rotation element to the transmission housing.
9. The planetary gear train of claim 8, wherein speed stages
implemented by selectively operating the first, second, third and
fourth clutches and the first and second brakes include: a first
forward speed stage, implemented by operating the first clutch, and
the first and second brakes; a second forward speed stage,
implemented by operating the third clutch, and the first and second
brakes; a third forward speed stage, implemented by operating the
first and third clutches, and the second brake; a fourth forward
speed stage, implemented by operating the second and third
clutches, and the second brake; a fifth forward speed stage,
implemented by operating the first and second clutches, and the
second brake; a sixth forward speed stage, implemented by operating
the first and fourth clutches, and the second brake; a seventh
forward speed stage, implemented by operating the first, third and
fourth clutches; an eighth forward speed stage, implemented by
operating the first and fourth clutches, and the first brake; a
ninth forward speed stage, implemented by operating the first and
second clutches, and the first brake; a forward tenth speed stage,
implemented by operating the second and fourth clutches, and the
first brake; and a reverse-speed stage, implemented by operating
the fourth clutch, and the first and second brakes.
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] The present application claims priority to Korean Patent
Application No. 10-2016-0032992, filed Mar. 18, 2016, the entire
contents of which is incorporated herein for all purposes by this
reference.
BACKGROUND OF THE INVENTION
[0002] 1. Field of the Invention
[0003] The present invention relates to an automatic transmission
for a vehicle. More particularly, the present invention relates to
a planetary gear train of an automatic transmission for a vehicle
that improves power delivery performance and fuel economy by
achieving ten forward speed stages with a minimum number of
constituent elements being used and improves silent driving of the
vehicle by using an operation point positioned at a low engine
speed.
[0004] 2. Description of Related Art
[0005] Generally, an automatic transmission achieving more speed
stages has been developed to enhance fuel economy and optimize
drivability. Recent increases in oil prices are triggering stiff
competition in enhancing fuel consumption of a vehicle.
[0006] Therefore, much research for reducing weight and enhancing
fuel economy through downsizing of an engine and for securing
drivability and fuel economy through multiple speed stages of
automatic transmissions has been developed.
[0007] However, in the automatic transmission, as the number of
speed stages increase, the number of internal components
(particularly, planetary gear sets) increase, and as a result, a
length of the transmission increases. This may deteriorate
installability and/or power flow efficiency and may increase
production cost, and weight.
[0008] Accordingly, development of a planetary gear train which may
achieve maximum efficiency with a small number of components is
important in order to increase a fuel economy enhancement effect
through the multiple speed-stages.
[0009] In this aspect, in recent years, 8-speed automatic
transmissions tend to be implemented and the research and
development of a planetary gear train capable of implementing more
speed stages has also been actively conducted.
[0010] However, a conventional 8-speed automatic transmission
typically includes three to four planetary gear sets and five to
six control elements (frictional elements). In this case, since the
length of the automatic transmission increases, mountability may be
deteriorated.
[0011] In recent planetary gear trains, one planetary gear set is
disposed above another planetary gear set, but structures of
automatic transmissions to which parallel planetary gear sets is
applied are very limited.
[0012] In other planetary gear trains, dog clutches instead of
control elements of wet-type are used. However, shift feel may be
deteriorated.
[0013] The information disclosed in this Background of the
Invention section is only for enhancement of understanding of the
general background of the invention and should not be taken as an
acknowledgement or any form of suggestion that this information
forms the prior art already known to a person skilled in the
art.
BRIEF SUMMARY
[0014] Various aspects of the present invention are directed to
providing a planetary gear train of an automatic transmission for a
vehicle having advantages of improving power delivery performance
and fuel economy by achieving at least ten forward speed stages and
one reverse speed stage.
[0015] In addition, various aspects of the present invention are
directed to providing a planetary gear train of an automatic
transmission for a vehicle having further advantages of improving
silent driving of the vehicle by using operation point positioned
at a low rotation speed region of an engine.
[0016] According to various aspects of the present invention, a
planetary gear train of an automatic transmission for a vehicle may
include an input shaft receiving torque of an engine, an output
shaft outputting torque of the engine, a first planetary gear set
including first, second, and third rotation elements, a second
planetary gear set including fourth, fifth, and sixth rotation
elements, a third planetary gear set including seventh, eighth, and
ninth rotation elements, a fourth planetary gear set including
tenth, eleventh, and twelfth rotation elements, a first shaft
connecting the first rotation element to the fourth rotation
element, a second shaft connecting the second rotation element to
the eighth rotation element and the twelfth rotation element, a
third shaft connected to the third rotation element, a fourth shaft
connected to the fifth rotation element and directly connected to
the input shaft, a fifth shaft connected to the sixth rotation
element and selectively connectable to the second shaft, a sixth
shaft connected to the seventh rotation element and selectively
connectable to the fifth shaft, a seventh shaft connecting the
ninth rotation element to the tenth rotation element and
selectively connectable to the fourth shaft and the fifth shaft,
and an eighth shaft connected to the eleventh rotation element and
directly connected to the output shaft.
[0017] The first shaft and the third shaft may each be selectively
connectable to a transmission housing.
[0018] The first, second, and third rotation elements may be a
first sun gear, a first planet carrier, and a first ring gear, the
fourth, fifth, and sixth rotation elements may be a second sun
gear, a second planet carrier, and a second ring gear, the seventh,
eighth, and ninth rotation elements may be a third sun gear, a
third planet carrier, and a third ring gear, and the tenth,
eleventh, and twelfth rotation elements comprise a fourth sun gear,
a fourth planet carrier, and a fourth ring gear.
[0019] The planetary gear train may further include a first clutch
selectively connecting the fourth shaft to the seventh shaft, a
second clutch selectively connecting the second shaft to the fifth
shaft, a third clutch selectively connecting the fifth shaft to the
seventh shaft, a fourth clutch selectively connecting the fifth
shaft to the sixth shaft, a first brake selectively connecting the
first shaft to the transmission housing, and a second brake
selectively connecting the third shaft to the transmission
housing.
[0020] According to various aspects of the present invention, a
planetary gear train of an automatic transmission for a vehicle may
include an input shaft receiving torque of an engine, an output
shaft outputting torque, a first planetary gear set including
first, second, and third rotation elements, a second planetary gear
set including fourth, fifth, and sixth rotation elements, a third
planetary gear set including seventh, eighth, and ninth rotation
elements, and a fourth planetary gear set including tenth,
eleventh, and twelfth rotation elements, in which the input shaft
may be directly connected to the fifth rotation element, the output
shaft may be directly connected to the eleventh rotation element,
the first rotation element may be directly connected to the fourth
rotation element, the second rotation element may be directly
connected to the eighth rotation element and the twelfth rotation
element, the sixth rotation element may be selectively connectable
to the second rotation element, the seventh rotation element may be
selectively connectable to the sixth rotation element, the ninth
rotation element may be selectively connectable to the fifth
rotation element and the sixth rotation element, and the tenth
rotation element may be directly connected to the ninth rotation
element and may be selectively connectable to the fifth rotation
element.
[0021] The first rotation element and the third rotation element
may each be selectively connectable to a transmission housing.
[0022] The planetary gear train may further include a first clutch
selectively connecting the fifth rotation element to the ninth
rotation element, a second clutch selectively connecting the second
rotation element to the sixth rotation element, a third clutch
selectively connecting the sixth rotation element to the ninth
rotation element, a fourth clutch selectively connecting the sixth
rotation element to the seventh rotation element, a first brake
selectively connecting the first rotation element to the
transmission housing, and a second brake selectively connecting the
third rotation element to the transmission housing.
[0023] Speed stages implemented by selectively operating the first,
second, third and fourth clutches and the first and second brakes
may include a forward first speed stage, implemented by operating
the first clutch, and the first and second brakes, a forward second
speed stage, implemented by operating the third clutch, and the
first and second brakes, a forward third speed stage, implemented
by operating the first and third clutches, and the second brake, a
forward fourth speed stage, implemented by operating the second and
third clutches, and the second brake, a forward fifth speed stage,
implemented by operating the first and second clutches, and the
second brake, a forward sixth speed stage, implemented by operating
the first and fourth clutches, and the second brake, a forward
seventh speed stage, implemented by operating the first, third and
fourth clutches, a forward eighth speed stage, implemented by
operating the first and fourth clutches, and the first brake, a
forward ninth speed stage, implemented by operating the first and
second clutches, and the first brake, a forward tenth speed stage,
implemented by operating the second and fourth clutches, and the
first brake, and a reverse-speed stage, implemented by operating
the fourth clutch, and the first and second brakes.
[0024] The planetary gear train according to various embodiments of
the present invention achieves ten forward speed stages and one
reverse speed stage by combining four planetary gear sets with six
control elements.
[0025] In addition, the planetary gear train according to various
embodiments of the present invention achieves speed stages suitable
to a rotation speed of the engine due to multiple-speed stages of
the automatic transmission. Particularly, silent driving of the
vehicle is improved by using operation point positioned at a low
rotation speed region of an engine.
[0026] Furthermore, the planetary gear train according to various
embodiments of the present invention maximizes driving efficiency
of the engine and improves power delivery performance and fuel
consumption.
[0027] It is understood that the term "vehicle" or "vehicular" or
other similar terms as used herein is inclusive of motor vehicles
in general such as passenger automobiles including sports utility
vehicles (SUV), buses, trucks, various commercial vehicles,
watercraft including a variety of boats and ships, aircraft, and
the like, and includes hybrid vehicles, electric vehicles, plug-in
hybrid electric vehicles, hydrogen-powered vehicles and other
alternative fuel vehicles (e.g., fuel derived from resources other
than petroleum). As referred to herein, a hybrid vehicle is a
vehicle that has two or more sources of power, for example, both
gasoline-powered and electric-powered vehicles.
[0028] The methods and apparatuses of the present invention have
other features and advantages which will be apparent from or are
set forth in more detail in the accompanying drawings, which are
incorporated herein, and the following Detailed Description, which
together serve to explain certain principles of the present
invention.
BRIEF DESCRIPTION OF THE DRAWINGS
[0029] FIG. 1 is a schematic diagram of a planetary gear train
according to various embodiments of the present invention.
[0030] FIG. 2 is an operation chart of control elements at each
speed stage in the planetary gear train according to various
embodiments of the present invention.
[0031] It should be understood that the appended drawings are not
necessarily to scale, presenting a somewhat simplified
representation of various features illustrative of the basic
principles of the invention. The specific design features of the
present invention as disclosed herein, including, for example,
specific dimensions, orientations, locations, and shapes will be
determined in part by the particular intended application and use
environment.
DETAILED DESCRIPTION
[0032] Reference will now be made in detail to various embodiments
of the present invention(s), examples of which are illustrated in
the accompanying drawings and described below. While the
invention(s) will be described in conjunction with exemplary
embodiments, it will be understood that the present description is
not intended to limit the invention(s) to those exemplary
embodiments. On the contrary, the invention(s) is/are intended to
cover not only the exemplary embodiments, but also various
alternatives, modifications, equivalents and other embodiments,
which may be included within the spirit and scope of the invention
as defined by the appended claims.
[0033] FIG. 1 is a schematic diagram of a planetary gear train
according to various embodiments of the present invention.
[0034] Referring to FIG. 1, a planetary gear train according to
various embodiments of the present invention includes first,
second, third, and fourth planetary gear sets PG1, PG2, PG3, and
PG4 disposed on the same axis, an input shaft IS, an output shaft
OS, eight rotation shafts TM1 to TM8 connected to at least one of
rotation elements of the first, second, third, and fourth planetary
gear sets PG1, PG2, PG3, and PG4, four clutches C1 to C4 and two
brakes B1 and B2 that are control elements, and a transmission
housing H.
[0035] Torque input from the input shaft IS is changed by
cooperation of the first, second, third, and fourth planetary gear
sets PG1, PG2, PG3, and PG4 and the changed torque is output
through the output shaft OS.
[0036] The planetary gear sets are disposed in the order of first,
second, third and fourth planetary gear sets PG1, PG2, PG3 and PG4
from an engine side.
[0037] The input shaft IS is an input member and the torque from a
crankshaft of an engine, after being torque-converted through a
torque converter, is input into the input shaft IS.
[0038] The output shaft OS is an output member, is disposed in
parallel with the input shaft IS, and transmits driving torque to a
driving wheel through a differential apparatus.
[0039] The first planetary gear set PG1 is a single pinion
planetary gear set and includes a first sun gear S1, a first planet
carrier PC1 rotatably supporting a first pinion P1 that is
externally meshed with the first sun gear S1, and a first ring gear
R1 that is internally meshed with the first pinion P1 respectively
as first, second, and third rotation elements N1, N2, and N3.
[0040] The second planetary gear set PG2 is a single pinion
planetary gear set and includes a second sun gear S2, a second
planet carrier PC2 rotatably supporting a second pinion P2 that is
externally meshed with the second sun gear S2, and a second ring
gear R2 that is internally meshed with the second pinion P2
respectively as fourth, fifth, and sixth rotation elements N4, N5,
and N6.
[0041] The third planetary gear set PG3 is a single pinion
planetary gear set and includes a third sun gear S3, a third planet
carrier PC3 rotatably supporting a third pinion P3 that is
externally meshed with the third sun gear S3, and a third ring gear
R3 that is internally meshed with the third pinion P3 respectively
as seventh, eighth, and ninth rotation elements N7, N8, and N9.
[0042] The fourth planetary gear set PG4 is a single pinion
planetary gear set and includes a fourth sun gear S4, a fourth
planet carrier PC4 rotatably supporting a fourth pinion P4 that is
externally meshed with the fourth sun gear S4, and a fourth ring
gear R4 that is internally meshed with the fourth pinion P4
respectively as tenth, eleventh, and twelfth rotation elements N10,
N11, and N12.
[0043] The first rotation element N1 is directly connected to the
fourth rotation element N4 the second rotation element N2 is
directly connected to the eighth rotation element N8 and the
twelfth rotation element N12, and the ninth rotation element N9 is
directly connected to the tenth rotation element N10 such that the
first, second, third, and fourth planetary gear sets PG1, PG2, PG3,
and PG4 include eight rotation shafts TM1 to TM8.
[0044] The eight rotation shafts TM1 to TM8 will be described in
detail.
[0045] The eight shafts TM1 to TM8 directly connect a plurality of
rotation elements among the rotation elements of the planetary gear
sets PG1, PG2, PG3, and PG4, are rotation members that are each
directly connected to at least one rotation element of the
planetary gear sets PG1, PG2, PG3, and PG4 and rotate with the at
least one rotation element to transmit torque, or are fixed members
that directly connect at least one rotation element of the
planetary gear sets PG1, PG2, PG3, and PG4 to the transmission
housing H to fix the at least one rotation element.
[0046] The first shaft TM1 directly connects the first rotation
element N1 (first sun gear S1) to the fourth rotation element N4
(second sun gear S2) and is selectively connectable to the
transmission housing H so as to be operated as a selective fixed
element.
[0047] The second shaft N2 directly connects the second rotation
element N2 (first planet carrier PC1) to the eighth rotation
element N8 (third planet carrier PC3) and the twelfth rotation
element N12 (fourth ring gear R4).
[0048] The third shaft TM3 is connected to the third rotation
element N3 (first ring gear R1) and is selectively connectable to
the transmission housing H so as to be operated as a selective
fixed element.
[0049] The fourth shaft TM4 is connected to the fifth rotation
element N5 (second planet carrier PC2) and is directly connected to
the input shaft IS so as to be continuously operated as an input
element.
[0050] The fifth shaft TM5 is connected to the sixth rotation
element N6 (second ring gear R2) and is selectively connectable to
the second shaft TM2.
[0051] The sixth shaft TM6 is connected to the seventh rotation
element N7 (third sun gear S3) and is selectively connectable to
the fifth shaft TM5.
[0052] The seventh shaft TM7 connects the ninth rotation element N9
(third ring gear R3) to the tenth rotation element N10 (fourth sun
gear S4) and is selectively connectable respectively to the fourth
shaft TM4 and the fifth shaft TM5.
[0053] The eighth shaft TM8 is connected to the eleventh rotation
element N11 (fourth planet carrier PC4) and is directly connected
to the output shaft OS so as to be continuously operated as an
output element.
[0054] In addition, four clutches C1, C2, C3, and C4 are disposed
at positions at which any two shafts among the eight shafts TM1 to
TM8 including the input shaft IS and the output shaft OS are
selectively connectable to each other.
[0055] In addition, two brakes B1 and B2 are disposed at positions
at which at least one shaft among the eight shafts TM1 to TM8 is
selectively connectable to the transmission housing H.
[0056] Arrangements of the four clutches C1 to C4 and the two
brakes B1 and B2 are described in detail.
[0057] The first clutch C1 is disposed between the fourth shaft TM4
and the seventh shaft TM7 and selectively connects the fourth shaft
TM4 to the seventh shaft TM7.
[0058] The second clutch C2 is disposed between the second shaft
TM2 and the fifth shaft TM5 and selectively connects the second
shaft TM2 to the fifth shaft TM5.
[0059] The third clutch C3 is disposed between the fifth shaft TM5
and the seventh shaft TM7 and selectively connects the fifth shaft
TM5 to the seventh shaft TM7.
[0060] The fourth clutch C4 is disposed between the fifth shaft TM5
and the sixth shaft TM6 and selectively connects the second shaft
TM2 to the sixth shaft TM6.
[0061] The first brake B1 is disposed between the first shaft TM1
and the transmission housing H and selectively connects the first
shaft TM1 to the transmission housing H.
[0062] The second brake B2 is disposed between the third shaft TM3
and the transmission housing H and selectively connects the third
shaft TM3 to the transmission housing H.
[0063] The control elements including the first, second, third, and
fourth clutches C1, C2, C3, and C4 and the first and second brakes
B1 and B2 may be multi-plates friction elements of wet type that
are operated by hydraulic pressure.
[0064] FIG. 2 is an operation chart of control elements at each
speed stage in the planetary gear train according to various
embodiments of the present invention.
[0065] As shown in FIG. 2, three control elements among the first,
second, third, and fourth clutches C1, C2, C3, and C4 and the first
and second brakes B1 and B2 that are control elements are operated
at each speed stage in the planetary gear train according to the
various embodiments of the present invention.
[0066] The first clutch C1 and the first and second brakes B1 and
B2 are operated at a first forward speed stage D1.
[0067] In a state that the fourth shaft TM4 is connected to the
seventh shaft TM7 by operation of the first clutch C1, torque of
the input shaft IS is input to the fourth shaft TM4.
[0068] In addition, the first shaft TM1 and the third shaft TM3 are
operated as the fixed elements by operation of the first brake B1
and the second brake B2. Therefore, the torque of the input shaft
IS is shifted into the first forward speed stage, and the first
forward speed stage is output through the output shaft OS connected
to the eighth shaft TM8.
[0069] The third clutch C3 and the first and second brakes B1 and
B2 are operated at a second forward speed stage D2.
[0070] In a state that the fifth shaft TM5 is connected to the
seventh shaft TM7 by operation of the third clutch C3, the torque
of the input shaft IS is input to the fourth shaft TM4.
[0071] In addition, the first shaft TM1 and the third shaft TM3 are
operated as the fixed elements by operation of the first brake B1
and the second brake B2. Therefore, the torque of the input shaft
IS is shifted into the second forward speed stage, and the second
forward speed stage is output through the output shaft OS connected
to the eighth shaft TM8.
[0072] The first and third clutches C1 and C3 and the second brake
B2 are operated at a third forward speed stage D3.
[0073] In a state that the fourth shaft TM4 is connected to the
seventh shaft TM7 by operation of the first clutch C1 and the fifth
shaft TM5 is connected to the seventh shaft TM7 by operation of the
third clutch C3, the torque of the input shaft IS is input to the
fourth shaft TM4.
[0074] In addition, the third shaft TM3 is operated as the fixed
element by operation of the second brake B2. Therefore, the torque
of the input shaft IS is shifted into the third forward speed
stage, and the third forward speed stage is output through the
output shaft OS connected to the eighth shaft TM8.
[0075] The second and third clutches C2 and C3 and the second brake
B2 are operated at a fourth forward speed stage D4.
[0076] In a state that the second shaft TM2 is connected to the
fifth shaft TM5 by operation of the second clutch C2 and the fifth
shaft TM5 is connected to the seventh shaft TM7 by operation of the
third clutch C3, the torque of the input shaft IS is input to the
fourth shaft TM4.
[0077] In addition, the third shaft TM3 is operated as the fixed
element by operation of the second brake B2. Therefore, the torque
of the input shaft IS is shifted into the fourth forward speed
stage, and the fourth forward speed stage is output through the
output shaft OS connected to the eighth shaft TM8.
[0078] The first and second clutches C1 and C2 and the second brake
B2 are operated at a fifth forward speed stage D5.
[0079] In a state that the fourth shaft TM4 is connected to the
seventh shaft TM7 by operation of the first clutch C1 and the
second shaft TM2 is connected to the fifth shaft TM5 by operation
of the second clutch C2, the torque of the input shaft IS is input
to the fourth shaft TM4.
[0080] In addition, the third shaft TM3 is operated as the fixed
element by operation of the second brake B2. Therefore, the torque
of the input shaft IS is shifted into the fifth forward speed
stage, and the fifth forward speed stage is output through the
output shaft OS connected to the eighth shaft TM8.
[0081] The first and fourth clutches C1 and C4 and the second brake
B2 are operated at a sixth forward speed stage D6.
[0082] In a state that the fourth shaft TM4 is connected to the
seventh shaft TM7 by operation of the first clutch C1 and the fifth
shaft TM5 is connected to the sixth shaft TM6 by operation of the
fourth clutch C4, the torque of the input shaft IS is input to the
fourth shaft TM4.
[0083] In addition, the third shaft TM3 is operated as the fixed
element by operation of the second brake B2. Therefore, the torque
of the input shaft IS is shifted into the sixth forward speed
stage, and the sixth forward speed stage is output through the
output shaft OS connected to the eighth shaft TM8.
[0084] The first, third, and fourth clutches C1, C3, and C4 are
operated at a seventh forward speed stage D7.
[0085] In a state that the fourth shaft TM4 is connected to the
seventh shaft TM7 by operation of the first clutch C1, the second
shaft TM2 is connected to the fifth shaft TM5 by operation of the
third clutch C3, and the fifth shaft TM5 is connected to the sixth
shaft TM6 by operation of the fourth clutch C4, the torque of the
input shaft IS is input to the fourth shaft TM4.
[0086] At this state, the planetary gear sets PG1, PG2, PG3, and
PG4 become lock-up states and the seventh forward speed stage is
output through the output shaft OS connected to the eighth shaft
TM8. At the seventh forward speed stage, the same rotation speed as
the input shaft IS is output.
[0087] The first and fourth clutches C1 and C4 and the first brake
B1 are operated at an eighth forward speed stage D8.
[0088] In a state that the fourth shaft TM4 is connected to the
seventh shaft TM7 by operation of the first clutch C1 and the fifth
shaft TM5 is connected to the sixth shaft TM6 by operation of the
fourth clutch C4, the torque of the input shaft IS is input to the
fourth shaft TM4.
[0089] In addition, the first shaft TM1 is operated as the fixed
element by operation of the first brake B1. Therefore, the torque
of the input shaft IS is shifted into the eighth forward speed
stage, and the eighth forward speed stage is output through the
output shaft OS connected to the eighth shaft TM8.
[0090] The first and second clutches C1 and C2 and the first brake
B1 are operated at a ninth forward speed stage D9.
[0091] In a state that the fourth shaft TM4 is connected to the
seventh shaft TM7 by operation of the first clutch C1 and the
second shaft TM2 is connected to the fifth shaft TM5 by operation
of the second clutch C2, the torque of the input shaft IS is input
to the fourth shaft TM4.
[0092] In addition, the first shaft TM1 is operated as the fixed
element by operation of the first brake B1. Therefore, the torque
of the input shaft IS is shifted into the ninth forward speed
stage, and the ninth forward speed stage is output through the
output shaft OS connected to the eighth shaft TM8.
[0093] The second and fourth clutches C2 and C4 and the first brake
B1 are operated at a tenth forward speed stage D10.
[0094] In a state that the second shaft TM2 is connected to the
fifth shaft TM5 by operation of the second clutch C2 and the fifth
shaft TM5 is connected to the sixth shaft TM6 by operation of the
fourth clutch C4, the torque of the input shaft IS is input to the
fourth shaft TM4.
[0095] In addition, the first shaft TM1 is operated as the fixed
element by operation of the first brake B1. Therefore, the torque
of the input shaft IS is shifted into the tenth forward speed
stage, and the tenth forward speed stage is output through the
output shaft OS connected to the eighth shaft TM8.
[0096] The fourth clutch C4 and the first and second brakes B1 and
B2 are operated at a reverse speed stage REV.
[0097] In a state that the fifth shaft TM5 is connected to the
sixth shaft TM6 by operation of the fourth clutch C4, the torque of
the input shaft IS is input to the fourth shaft TM4.
[0098] In addition, the first shaft TM1 and the third shaft TM3 are
operated as the fixed elements by operation of the first brake B1
and the second brake B2. Therefore, the torque of the input shaft
IS is shifted into the reverse speed stage, and the reverse speed
stage is output through the output shaft OS connected to the eighth
shaft TM8.
[0099] The planetary gear trains according to various embodiments
of the present invention achieves at least ten forward speed stages
and one reverse speed stage by combining four planetary gear sets
PG1, PG2, PG3, and PG4 with the four clutches C1, C2, C3, and C4
and the two brakes B1 and B2.
[0100] In addition, the planetary gear train according to various
embodiments of the present invention achieves suitable speed stages
according to rotation speed of the engine. Particularly, silent
driving of the vehicle is improved by using operation point
positioned at a low rotation speed region of the engine.
[0101] Furthermore, the planetary gear train according to various
embodiments of the present invention maximizes driving efficiency
of the engine and improves power delivery performance and fuel
consumption.
[0102] The foregoing descriptions of specific exemplary embodiments
of the present invention have been presented for purposes of
illustration and description. They are not intended to be
exhaustive or to limit the invention to the precise forms
disclosed, and obviously many modifications and variations are
possible in light of the above teachings. The exemplary embodiments
were chosen and described in order to explain certain principles of
the invention and their practical application, to thereby enable
others skilled in the art to make and utilize various exemplary
embodiments of the present invention, as well as various
alternatives and modifications thereof. It is intended that the
scope of the invention be defined by the Claims appended hereto and
their equivalents.
* * * * *