U.S. patent application number 14/956344 was filed with the patent office on 2017-03-16 for planetary gear train of automatic transmission for vehicles.
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, Dong Hwan Hwang, Seong Wook Hwang, Seongwook Ji, SeokJin Kim, Hyun Sik Kwon, Chang Wook Lee, KyeongHun Lee, JongSool Park.
Application Number | 20170074371 14/956344 |
Document ID | / |
Family ID | 58163546 |
Filed Date | 2017-03-16 |
United States Patent
Application |
20170074371 |
Kind Code |
A1 |
Park; JongSool ; et
al. |
March 16, 2017 |
PLANETARY GEAR TRAIN OF AUTOMATIC TRANSMISSION FOR VEHICLES
Abstract
A planetary gear train of an automatic transmission may include
an input shaft; an output shaft; first to fourth planetary gear
sets and six control elements disposed at a portion selectively
connecting the rotation elements and the rotation elements or a
portion selectively connecting the rotation elements and the
transmission housing, wherein the input shaft is continuously
connected to the third rotation element, the output shaft is
continuously connected to the twelfth rotation element, the first
rotation element is continuously connected to the transmission
housing, the fourth rotation element is continuously connected to
the seventh rotation element, the fourth rotation element is
continuously connected to the tenth rotation element, the eighth
rotation element is continuously connected to the twelfth rotation
element, the fifth rotation element is selectively connected to the
transmission housing.
Inventors: |
Park; JongSool;
(Hwaseong-Si, KR) ; Hwang; Dong Hwan; (Seoul,
KR) ; Hwang; Seong Wook; (Gunpo-Si, KR) ; Ji;
Seongwook; (Ansan-Si, KR) ; Lee; Chang Wook;
(Suwon-Si, KR) ; Kwon; Hyun Sik; (Seoul, KR)
; Kim; SeokJin; (Hwaseong-Si, KR) ; Lee;
KyeongHun; (Seoul, KR) ; Cho; Wonmin;
(Hwaseong-Si, KR) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Hyundai Motor Company |
Seoul |
|
KR |
|
|
Assignee: |
Hyundai Motor Company
Seoul
KR
|
Family ID: |
58163546 |
Appl. No.: |
14/956344 |
Filed: |
December 1, 2015 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F16H 2200/2046 20130101;
F16H 2200/2012 20130101; F16H 2200/0065 20130101; F16H 2200/2097
20130101; F16H 3/66 20130101 |
International
Class: |
F16H 3/66 20060101
F16H003/66 |
Foreign Application Data
Date |
Code |
Application Number |
Sep 14, 2015 |
KR |
10-2015-0129867 |
Claims
1. A planetary gear train of an automatic transmission for a
vehicle comprising: an input shaft receiving power of an engine; an
output shaft outputting shifted power; a first planetary gear set
having a first rotation element, a second rotation element, and a
third rotation element; a second planetary gear set having a fourth
rotation element, a fifth rotation element, and a sixth rotation
element; a third planetary gear set having a seventh rotation
element, an eighth rotation element, and a ninth rotation element;
a fourth planetary gear set having a tenth rotation element, an
eleventh rotation element, and a twelfth rotation element; and six
control elements disposed at a portion selectively connecting the
rotation elements and the rotation elements or a portion
selectively connecting the rotation elements and a transmission
housing, wherein the input shaft is continuously connected to the
third rotation element, the output shaft is continuously connected
to the twelfth rotation element, the first rotation element is
continuously connected to the transmission housing, the fourth
rotation element is continuously connected to the seventh rotation
element, the fourth rotation element is continuously connected to
the tenth rotation element, the eighth rotation element is
continuously connected to the twelfth rotation element, the fifth
rotation element is selectively connected to the transmission
housing, while three control elements of the six control elements
are operated, at least nine forward speed stages and at least one
reverse speed stage are implemented.
2. The planetary gear train of claim 1, wherein the ninth rotation
element is selectively connected to the transmission housing the
input shaft is selectively connected to the fifth rotation element,
the input shaft is selectively connected to the eleventh rotation
element, the fifth rotation element is selectively connected to the
sixth rotation element, the second rotation element is selectively
connected to the sixth rotation element.
3. The planetary gear train of claim 1, wherein the first rotation
element, the second rotation element, and the third rotation
element of the first planetary gear set are a sun gear, a planetary
carrier, and a ring gear, respectively, the fourth rotation
element, the fifth rotation element, and the sixth rotation element
of the second planetary gear set are a sun gear, a planetary
carrier, and a ring gear, the seventh rotation element, the eighth
rotation element, and the ninth rotation element of the third
planetary gear set are a sun gear, a planetary carrier, and a ring
gear, respectively, the tenth rotation element, the eleventh
rotation element, and the twelfth rotation element of the fourth
planetary gear set are a sun gear, a planetary carrier, and a ring
gear, respectively.
4. A planetary gear train of an automatic transmission for a
vehicle comprising: an input shaft receiving power of an engine; an
output shaft outputting shifted power; a first planetary gear set
having a first rotation element, a second rotation element, and a
third rotation element; a second planetary gear set having a fourth
rotation element, a fifth rotation element, and a sixth rotation
element; a third planetary gear set having a seventh rotation
element, an eighth rotation element, and a ninth rotation element;
a fourth planetary gear set having a tenth rotation element, an
eleventh rotation element, and a twelfth rotation element; and six
control elements disposed at a portion selectively connecting the
rotation elements and the rotation elements or a portion
selectively connecting the rotation elements and a transmission
housing; a first rotating shaft including the first rotation
element and directly connected to the transmission housing; a
second rotating shaft including the second rotation element; a
third rotating shaft including the third rotation element and
directly connected to the input shaft; a fourth rotating shaft
including the fourth rotation element, the seventh rotation
element, and the tenth rotation element; a fifth rotating shaft
including the fifth rotation element and selectively connected to
the third rotating shaft including the input shaft and
simultaneously connected to the transmission housing; a sixth
rotating shaft including the sixth rotation element and selectively
connected to the second rotating shaft and the fifth rotating
shaft; a seventh rotating shaft including the eighth rotation
element and the twelfth rotation element and directly connected to
the output shaft; a eighth rotating shaft including the ninth
rotation element and selectively connected to the transmission
housing; and a ninth rotating shaft including the eleventh rotation
element and selectively connected to the third rotating shaft
including the input shaft.
5. The planetary gear train of claim 4, wherein the first planetary
gear set is a single-pinion planetary gear set, in which the first
rotation element is a first sun gear, the second rotation element
is a first planet carrier, and the third rotation element is a
first ring gear, the second planetary gear set is a single-pinion
planetary gear set, in which the fourth rotation element is a
second sun gear, the fifth rotation element is a second planet
carrier, and the sixth rotation element is a second ring gear, the
third planetary gear set is a single-pinion planetary gear set, in
which the seventh rotation element is a third sun gear, the eighth
rotation element is a third planet carrier, and the ninth rotation
element is a third ring gear, and the fourth planetary gear set is
a single-pinion planetary gear set, the tenth rotation element is a
fourth sun gear, the eleventh rotation element is a fourth planet
carrier, and the twelfth rotation element is a fourth ring
gear.
6. The planetary gear train of claim 4, wherein the six control
elements includes: a first clutch selectively connecting the third
rotating shaft and the fifth rotating shaft; a second clutch
selectively connecting the third rotating shaft and the ninth
rotating shaft; a third clutch selectively connecting the fifth
rotating shaft and the sixth rotating shaft; a fourth clutch
selectively connecting the second rotating shaft and the sixth
rotating shaft; a first brake selectively connecting the fifth
rotating shaft and the transmission housing; and a second brake
selectively connecting the eighth rotating shaft and the
transmission housing.
7. The planetary gear train of claim 6, wherein speed stages
realized by the selective operation of the six control elements
include a first forward speed stage by a simultaneous operation of
the third and fourth clutches and the second brake; a second
forward speed stage by a simultaneous operation of the first and
third clutches and the second brake; a third forward speed stage by
a simultaneous operation of the first and fourth clutches and the
second brake; a fourth forward speed stage by a simultaneous
operation of the first clutch and the second clutch and the second
brake; a fifth forward speed stage by a simultaneous operation of
the first, second, and fourth clutches; a sixth forward speed stage
by a simultaneous operation of the first, second, and third
clutches; a seventh forward speed stage by a simultaneous operation
of the second, third, and fourth clutches; an eighth forward speed
stage by a simultaneous operation of the second and third clutches
and the first brake; a ninth forward speed stage by a simultaneous
operation of the second and fourth clutches and the first brake;
and a reverse speed stage by a simultaneous operation of the fourth
clutch and the first and second brakes.
8. A planetary gear train of an automatic transmission for a
vehicle comprising: an input shaft receiving power of an engine; an
output shaft outputting shifted power; a first planetary gear set
made of a single pinion planetary gear set and including a a first
rotation element, a second rotation element, and a third rotation
element; a second planetary gear set made of a single pinion
planetary gear set and including a a fourth rotation element, a
fifth rotation element, and a sixth rotation element; a third
planetary gear set made of a single pinion planetary gear set and
including a a seventh rotation element, an eighth rotation element,
and a ninth rotation element; and a fourth planetary gear set made
of a single pinion planetary gear set and including a a tenth
rotation element, an eleventh rotation element, and a twelfth
rotation element, a first rotating shaft including the first
rotation element and directly connected to a transmission housing;
a second rotating shaft including the second rotation element; a
third rotating shaft including the third rotation element and
directly connected to the input shaft; a fourth rotating shaft
including the fourth rotation element, the seventh rotation
element, and the tenth rotation element; a fifth rotating shaft
including the fifth rotation element and selectively connected to
the third rotating shaft including the input shaft and
simultaneously to the transmission housing; a sixth rotating shaft
including the sixth rotation element and selectively connected to
the second rotating shaft and the fifth rotating shaft; a seventh
rotating shaft including the eighth rotation element and the
twelfth rotation element and directly connected to the output
shaft; an eighth rotating shaft including the ninth rotation
element and selectively connected to the transmission housing; a
ninth rotating shaft including the eleventh rotation element and
selectively connected to the third rotating shaft including the
input shaft; a first clutch selectively connecting the third
rotating shaft and the fifth rotating shaft; a second clutch
selectively connecting the third rotating shaft and the ninth
rotating shaft; a third clutch selectively connecting the fifth
rotating shaft and the sixth rotating shaft; a fourth clutch
selectively connecting the second rotating shaft and the sixth
rotating shaft; a first brake selectively connecting the fifth
rotating shaft and the transmission housing; and a second brake
selectively connecting the eighth rotating shaft and the
transmission housing.
9. The planetary gear train of claim 8, wherein the first planetary
gear set includes the first rotation element made of the first sun
gear, the second rotation element made of the first planetary
carrier, and the third rotation element made of the first ring
gear, the second planetary gear set includes the fourth rotation
element made of the second sun gear, the fifth rotation element
made of the second planetary carrier, and the sixth rotation
element made of the second ring gear, the third planetary gear set
includes the seventh rotation element made of the third sun gear,
the eighth rotation element made of the third planetary carrier,
and ninth rotation element made of the third ring gear, and the
fourth planetary gear set includes the tenth rotation element made
of the fourth sun gear, the eleventh rotation element made of the
fourth planetary carrier, and the twelfth rotation element made of
the fourth ring gear.
10. The planetary gear train of claim 8, wherein the speed stages
realized by the selective operation of four clutches and two brakes
include: a first forward speed stage by a simultaneous operation of
the third and fourth clutches and the second brake; a second
forward speed stage by a simultaneous operation of the first and
third clutches and the second brake; a third forward speed stage by
a simultaneous operation of the first and fourth clutches and the
second brake; a fourth forward speed stage by a simultaneous
operation of the first clutch and the second clutch and the second
brake; a fifth forward speed stage by a simultaneous operation of
the first, second, and fourth clutches; a sixth forward speed stage
by a simultaneous operation of the first, second, and third
clutches; a seventh forward speed stage by a simultaneous operation
of the second, third, and fourth clutches; an eighth forward speed
stage by a simultaneous operation of the second and third clutches
and the first brake; a ninth forward speed stage by a simultaneous
operation of the second and fourth clutches and the first brake;
and a reverse speed stage by a simultaneous operation of the fourth
clutch and the first and second brakes.
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] The present application claims priority to and the benefit
of Korean Patent Application No. 10-2015-0129867 filed on Sep. 14,
2015, the entire contents of which is incorporated herein for all
purposes by this reference.
BACKGROUND OF THE INVENTION
[0002] Field of the Invention
[0003] The present invention relates to an automatic transmission
for a vehicle. More particularly, the present invention relates to
that improves power delivery performance and fuel consumption and
obtains a linearity between step ratios of transmission steps by
enlarging a span of gear ratios while achieving nine forward speed
stages using a minimum number of constituent elements.
[0004] Description of Related Art
[0005] The recent increase in oil prices causes carmakers to meet
global demands of improving fuel efficiency.
[0006] Accordingly, researches are being conducted on engines in
terms of reducing weight and improving fuel efficiency by
down-sizing, and researches are also being conducted to ensure both
drivability and competitiveness by maximizing fuel efficiency by
implementing an automatic transmission with multiple stages.
[0007] However, in the case of the automatic transmission, the
number of internal components is increased as the number of gear
shift stages is increased, which may cause deterioration in terms
of mountability, costs, weight and power transmission
efficiency.
[0008] Therefore, in order to increase an effect of improving fuel
efficiency by implementing an automatic transmission with multiple
stages, it is important to develop a planetary gear train capable
of maximizing efficiency using a small number of components.
[0009] In this respect, recently, an eight-speed automatic
transmission has been implemented, and researches and developments
are being actively conducted on a planetary gear train that may
implement gear shift stages for eight or more speeds.
[0010] However, in the case of the recent eight-speed automatic
transmission, a span of a gear shift ratio is maintained at a level
of 6.5 to 7.5, and as a result, there is a problem in that the
recent eight-speed automatic transmission has no great effect of
improving fuel efficiency.
[0011] In a case in which a span of a gear shift ratio in the
eight-speed automatic transmission is increased to the level of 9.0
or more, because it is impossible to ensure linearity of step
ratios between gear shift stages, driving efficiency of the engine
and drivability of the vehicle deteriorate.
[0012] Accordingly, there is a need for development of a highly
efficient automatic transmission with 9 or more forward speed
stages.
[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 that improves power delivery performance and fuel
efficiency and ensures linearity of step ratios between
transmission steps by increasing a span of gear ratios while
realizing at least nine forward speed or more stages and at least
one reverse speed or more stage by using a minimum number of
constituent elements.
[0015] A planetary gear train of an automatic transmission for
vehicles according to the present invention includes an input shaft
receiving power of an engine; an output shaft outputting shifted
power; a first planetary gear set having first, second, and third
rotation elements; a second planetary gear set having fourth,
fifth, and sixth rotation elements; a third planetary gear set
having seventh, eighth, and ninth rotation elements; a fourth
planetary gear set having tenth, eleventh, and twelfth rotation
elements; and six control elements disposed at a portion
selectively connecting the rotation elements and the rotation
elements or a portion selectively connecting the rotation elements
and the transmission housing, wherein the input shaft is
continuously connected to the third rotation element, the output
shaft is continuously connected to the twelfth rotation element,
the first rotation element is continuously connected to the
transmission housing, the fourth rotation element is continuously
connected to the seventh rotation element, the fourth rotation
element is continuously connected to the tenth rotation element,
the eighth rotation element is continuously connected to the
twelfth rotation element, the fifth rotation element is selectively
connected to the transmission housing, while three control elements
of the six control elements are operated, at least nine forward
speed stages and at least one reverse speed stage are
implemented.
[0016] The ninth rotation element may be selectively connected to
the transmission housing, the input shaft may be selectively
connected to the fifth rotation element, the input shaft may be
selectively connected to the eleventh rotation element, the fifth
rotation element may be selectively connected to the sixth rotation
element, and the second rotation element may be selectively
connected to the sixth rotation element.
[0017] The first, second, and third rotation elements of the first
planetary gear set may be a sun gear, a planetary carrier, and a
ring gear, respectively, the fourth, fifth, and sixth rotation
elements of the second planetary gear set may be a sun gear, a
planetary carrier, and a ring gear, the seventh, eighth, and ninth
rotation elements of the third planetary gear set may be a sun
gear, a planetary carrier, and a ring gear, respectively, and the
tenth, eleventh, and twelfth rotation elements of the fourth
planetary gear set may be a sun gear, a planetary carrier, and a
ring gear, respectively.
[0018] The planetary gear train according to an exemplary
embodiment of the present invention may implement the gear shift
stages for nine forward speed stages and one reverse speed stage by
combining four planetary gear sets with the six control
elements.
[0019] In addition, a span of a gear shift ratio is 9.0 or more,
thereby maximizing driving efficiency of the engine.
[0020] In addition, the linearity of the interstage ratio of the
shift stage is secured while multi-staging the shift stage at high
efficiency, thereby making it possible to improve drivability such
as acceleration before and after the shift, an engine speed
rhythmic sense, and the like.
[0021] Further, effects that can be obtained or expected from
exemplary embodiments of the present invention are directly or
suggestively described in the following detailed description. That
is, various effects expected from exemplary embodiments of the
present invention will be described in the following detailed
description.
[0022] 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
[0023] FIG. 1 is a configuration diagram of a planetary gear train
according to a first exemplary embodiment of the present
invention.
[0024] FIG. 2 is an operation table for each of transmission steps
of respective control elements applied to the planetary gear train
according to the first exemplary embodiment of the present
invention.
[0025] 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.
[0026] In the figures, reference numbers refer to the same or
equivalent parts of the present invention throughout the several
figures of the drawing.
DETAILED DESCRIPTION
[0027] 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.
[0028] The present invention will be described more fully
hereinafter with reference to the accompanying drawings, in which
exemplary embodiments of the invention are shown. As those skilled
in the art would realize, the described embodiments may be modified
in various different ways, all without departing from the spirit or
scope of the present invention.
[0029] However, parts which are not related with the description
are omitted for clearly describing the exemplary embodiment of the
present invention, and like reference numerals refer to like or
similar elements throughout the specification.
[0030] In the following description, dividing names of components
into first, second, and the like is to divide the names because the
names of the components are the same as each other, and an order
thereof is not particularly limited.
[0031] FIG. 1 is a configuration diagram of a planetary gear train
according to a first exemplary embodiment of the present
invention.
[0032] Referring to FIG. 1, the planetary gear train according to
an exemplary embodiment of the present invention includes first,
second, third, fourth planetary gear sets PG1, PG2, PG3, and PG4
disposed on the same axis, an input shaft IS, an output shaft OS,
nine rotating shafts TM1 to TM9 directly connecting to each other
through respective rotation elements of the first, second, third,
and fourth planetary gear sets PG1, PG2, PG3, and PG4, six control
elements C1-C4 and B1-B2, and a transmission housing H.
[0033] As a result, torque input from the input shaft IS is
transmitted by an inter-complementation operation of the first,
second, third, and fourth planetary gear sets PG1, PG2, PG3, and
PG4 to be output through the output shaft OS.
[0034] The respective simple planetary gear sets are disposed in a
sequence of the first, second, third, and fourth planetary gear
sets PG1, PG2, PG3, and PG4 from an engine side.
[0035] The input shaft IS is an input member, and rotational power
from a crankshaft of an engine is torque-converted through a torque
converter to be input into the input shaft IS.
[0036] The output shaft OS is an output member, is disposed on the
same axis as the input shaft IS, and transfers transmitted driving
torque to a driving shaft through a differential apparatus.
[0037] The first planetary gear set PG1 is a single pinion
planetary gear set, and includes rotation elements including a
first sun gear S1 which is a first rotation element N1, a first
planet carrier PC1 which is a second rotation element N2 for
supporting a first pinion P1 that externally engages with the first
sun gear S1 that is the first rotation element N1, and a first ring
gear R1 which is a third rotation element N3 that internally
engages with the first pinion P1.
[0038] The second planetary gear set PG2 is a single pinion
planetary gear set, and includes a second sun gear S2 which is a
fourth rotation element N4, a second planet carrier PC2 which is a
fifth rotation element N5 for supporting a second pinion P2 that
externally engages with the second sun gear S2 that is the fourth
rotation element N4, and a second ring gear R2 which is a sixth
rotation element N6 that internally engages with the second pinion
P2.
[0039] The third planetary gear set PG3 is a single pinion
planetary gear set, and includes a third sun gear S3 which is a
seventh rotation element N7, a third planet carrier PC3 which is an
eighth rotation element N8 for supporting a third pinion P3 that
externally engages with the third sun gear S3 that is the seventh
rotation element N7, and a third ring gear R3 which is a ninth
rotation element N9 that internally engages with the third pinion
P3.
[0040] The fourth planetary gear set PG4 is a single pinion
planetary gear set and includes a fourth sun gear S4 which is a
tenth rotation element N10, a fourth planet carrier PC4 which is an
eleventh rotation element N11 for supporting a fourth pinion P4
that externally engages with the fourth sun gear S4 that is the
tenth rotation element N10, and a fourth ring gear R4 which is a
twelfth rotation element N12 that internally engages with the
fourth pinion P4.
[0041] The first, second, third, and fourth planetary gear sets
PG1, PG2, PG3, and PG4 are operated while the fourth rotation
element N4 is directly connected to the seventh rotation element N7
and the tenth rotation element N10, and the eighth rotation element
N8 is directly connected to the twelfth rotation element N12 and
total nine rotating shafts TM1-TM9.
[0042] The configurations of the nine rotating shafts TM1 to TM9
will be described below.
[0043] The first rotating shaft TM1 includes a first rotation
element N1 (a first sun gear S1) and is directly connected to the
transmission housing H.
[0044] The second rotating shaft TM2 includes a second rotation
element N2 (a first planetary carrier PC1).
[0045] The third rotating shaft TM3 includes a third rotation
element N3 (a first ring gear R1) and i directly connected to the
input shaft IS.
[0046] The fourth rotating shaft TM4 includes a fourth rotation
element N4 (a second sun gear N2), a seventh rotation element N7 (a
third sun gear N3), a tenth rotation element N10 (a fourth sun gear
N4).
[0047] The fifth rotating shaft TM5 includes a fifth rotation
element N5 (a second planetary carrier PC2) and is selectively
connected to the third rotating shaft TM3 including the input shaft
IS and simultaneously is selectively connected to the transmission
housing H.
[0048] The sixth rotating shaft TM6 includes a sixth rotation
element N6 (a second ring gear R2) and is selectively connected to
the second rotating shaft TM2 and the fifth rotating shaft TM5.
[0049] The seventh rotating shaft TM7 includes the eighth rotation
element N8 (a third planetary carrier PC3) and the twelfth rotation
element N12 (a fourth ring gear R4) and is directly connected to
the output shaft OS to be operated as an output element.
[0050] The eighth rotating shaft TM8 includes the ninth rotation
element N9 (a third ring gear R3) and is selectively connected to
the transmission housing H.
[0051] The ninth rotating shaft TM9 includes the eleventh rotation
element N11 (a third planetary carrier PC3) and is selectively
connected to the third rotating shaft TM3 including the input shaft
IS.
[0052] Further, four clutches C1, C2, C3, and C4, which are control
elements, are disposed at portions where the rotating shafts of the
rotating shafts TM1 to TM9 are selectively connected to each
other.
[0053] In addition, two brakes Bland B2, which are control
elements, are disposed at portions where the rotating shafts of the
rotating shafts TM1 to TM9 are selectively connected with the
transmission housing H.
[0054] The arrangement positions of the six control elements C1-C4
and B1-B2 will be described below.
[0055] The first clutch C1 is disposed between the third rotating
shaft TM3 including the input shaft IS and the fifth rotating shaft
TM5 to selectively integrate the third rotating shaft TM3 and the
fifth rotating shaft TM5.
[0056] The second clutch C2 is disposed between the third rotating
shaft TM3 including the input shaft IS and the ninth rotating shaft
TM9 to selectively integrate the third rotating shaft TM3 and the
ninth rotating shaft TM9.
[0057] The third clutch C3 is interposed between the fifth rotating
shaft TM5 and the sixth rotating shaft TM6 to selectively integrate
the fifth rotating shaft TM5 and the sixth rotating shaft TM6.
[0058] The fourth clutch C4 is interposed between the second
rotating shaft TM2 and the sixth rotating shaft TM6 to selectively
integrate the second rotating shaft TM2 and the sixth rotating
shaft TM6.
[0059] The first brake B1 is interposed between the fifth rotating
shaft TM5 and the transmission housing H to selectively operate the
fifth rotating shaft TM5 as a fixing element.
[0060] The second brake B2 is interposed between the eighth
rotating shaft TM8 and the transmission housing H to selectively
operate the eighth rotating shaft TM8 as a fixing element.
[0061] The respective 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 formed of a multi-plate type
hydraulic friction coupling unit which is frictionally coupled by
hydraulic pressure.
[0062] FIG. 2 is an operation table for each of transmission steps
of respective control elements applied to the planetary gear train
according to the first exemplary embodiment of the present
invention.
[0063] As shown in FIG. 2, the planetary gear train according to
the exemplary embodiment of the present invention is shifted while
three control elements are operated in each shift stage.
[0064] At the first forward speed stage D1, the third and fourth
clutches C3 and C4 and the second brake B2 are simultaneously
operated. Therefore, in a state in which the sixth rotating shaft
TM6 is connected to the sixth rotating shaft TM6 to each other by
the operation of the third clutch C3 and the second rotating shaft
TM2 is connected to the sixth rotating shaft TM6 by the operation
of the fourth clutch C4, the power is inputted to the third
rotating shaft TM3, while the first rotating shaft TM1 is operated
as a fixing element and simultaneously the eighth rotating shaft
TM8 is operated as a fixing element by the operation of the second
brake B2, the first forward speed is realized and the power is
output through the output shaft OS including the seventh rotating
shaft TM7.
[0065] At the second forward speed stage D2, the first and third
clutches C1 and C3 and the second brake B2 are simultaneously
operated. Therefore, in a state in which the third rotating shaft
TM3 including the input shaft IS is connected to the fifth rotating
shaft TM5 by the operation of the first clutch C1 and the fifth
rotating shaft TM5 is connected to the sixth rotating shaft TM6 to
each other by the operation of the third clutch C3, the power is
simultaneously inputted to the third rotating shaft TM3 and the
fifth rotating shaft TM5, while the first rotating shaft TM1 is
operated as a fixing element and simultaneously the eighth rotating
shaft TM8 is operated as a fixing element by the operation of the
second brake B2, the second forward speed is realized and the power
is output through the output shaft OS including the seventh
rotating shaft TM7.
[0066] At the third forward speed stage D3, the first and fourth
clutches C1 and C4 and the second brake B2 are simultaneously
operated. Therefore, in a state in which the third rotating shaft
TM3 including the input shaft IS is connected to the fifth rotating
shaft TM5 to each other by the operation of the first clutch C1 and
the second rotating shaft TM2 is connected to the sixth rotating
shaft TM6 to each other by the operation of the fourth clutch C4,
the power is simultaneously inputted to the third rotating shaft
TM3 and the fifth rotating shaft TM5, while the first rotating
shaft TM1 is operated as a fixing element and simultaneously the
eighth rotating shaft TM8 is operated as a fixing element by the
operation of the second brake B2, the third forward speed is
realized and the power is output through the output shaft OS
including the seventh rotating shaft TM7.
[0067] At the fourth forward speed stage D4, the first and second
clutches C1 and C2 and the second brake B2 are simultaneously
operated. Therefore, in a stage in which the third rotating shaft
TM3 including the input shaft IS is connected to the fifth rotating
shaft TM5 to each other by the operation of the first clutch C1 and
the third rotating shaft TM3 including the input shaft IS is
connected to the ninth rotating shaft TM9 to each other by the
operation of the second clutch C2, the power is simultaneously
inputted to the third, fifth, and ninth rotating shafts TM3, TM5,
and TM9, while the first rotating shaft TM1 is operated as a fixing
element and simultaneously the eighth rotating shaft TM8 is
operated as a fixing element by the operation of the second brake
B2, the fourth forward speed is realized and the power is output
through the output shaft OS including the seventh rotating shaft
TM7.
[0068] At the fifth forward speed stage D5, the first, second, and
fourth clutches C1, C2, and C4 are simultaneously operated.
Therefore, in a state in which the third rotating shaft TM3
including the input shaft IS is connected to the fifth rotating
shaft TM5 to each other by the operation of the first clutch C1,
the third rotating shaft TM3 including the input shaft IS is
connected to the ninth rotating shaft TM9 to each other by the
operation of the second clutch C2, and the second rotating shaft
TM2 is connected to the sixth rotating shaft TM6 to each other by
the operation of the fourth clutch C4, the power is simultaneously
inputted to the third, fifth, and ninth rotating shafts TM3, TM5,
and TM9, while the first rotating shaft TM1 is operated as a fixing
element, the fifth forward speed is realized and the power is
output through the output shaft OS including the seventh rotating
shaft TM7.
[0069] At the sixth forward speed stage D6, the first, second, and
third clutches C1, C2, and C3 are simultaneously operated.
Therefore, in a state in which the third rotating shaft TM3
including the input shaft IS is connected to the fifth rotating
shaft TM5 to each other by the operation of the first clutch C1,
the third rotating shaft TM3 including the input shaft IS is
connected to the ninth rotating shaft TM9 to each other by the
operation of the second clutch C2, and the fifth rotating shaft TM5
is connected to the sixth rotating shaft TM6 to each other by the
operation of the third clutch C3, the power is simultaneously
inputted to the third, fifth, ninth rotating shaft TM3, TM5, and
TM9, while the first rotating shaft TM1 is operated as a fixing
element, the sixth forward speed is realized and the power is
output through the output shaft OS including the seventh rotating
shaft TM7.
[0070] At the seventh forward speed stage D7, the second, third,
and fourth clutches C2, C3, and C4 are simultaneously operated.
Therefore, in a state in which the third rotating shaft TM3
including the input shaft IS is connected to the ninth rotating
shaft TM9 to each other by the operation of the second clutch C2,
the fifth rotating shaft TM5 connected to the sixth rotating shaft
TM6 to each other by the operation of the third clutch C3, and
second rotating shaft TM2 is connected to the sixth rotating shaft
TM6 to each other by the operation of the fourth clutch C4, the
power is simultaneously inputted to the third and ninth rotating
shafts TM3 and TM9, while first rotating shaft TM1 is operated as a
fixing element, the seventh forward speed is realized and the power
is output through the output shaft OS including the seventh
rotating shaft TM7.
[0071] At the eighth forward speed stage D8, the second and third
clutches C2 and C3 and the first brake B1 are simultaneously
operated. Therefore, in a state in which the third rotating shaft
TM3 including the input shaft IS is connected to the ninth rotating
shaft TM9 to each other by the operation of the second clutch C2
and the fifth rotating shaft TM5 is connected to the sixth rotating
shaft TM6 to each other by the operation of the third clutch C3,
the power is inputted to the third and ninth rotating shafts TM3
and TM9, while the first rotating shaft TM1 is operated as a fixing
element and simultaneously the fifth rotating shaft TM5 is operated
as a fixing element by the operation of the first brake B1, the
eighth forward speed is realized and the power is output through
the output shaft OS including the seventh rotating shaft TM7.
[0072] At the ninth forward speed stage D9, the second and fourth
clutches C2 and C4 and the first brake B1 are simultaneously
operated. Therefore, in a state in which the third rotating shaft
TM3 including the input shaft IS is connected to the ninth rotating
shaft TM9 to each other by the operation of the second clutch C2
and the second rotating shaft TM2 is connected to the sixth
rotating shaft TM6 to each other by the operation of the fourth
clutch C4, the power is inputted to the third and ninth rotating
shafts TM3 and TM9, while the first rotating shaft TM1 is operated
as a fixing element and simultaneously the fifth rotating shaft TM5
is operated as a fixing element by the operation of the first brake
B1, the ninth forward speed is realized and the power is output
through the output shaft OS including the seventh rotating shaft
TM7.
[0073] At the reverse speed stage REV, the fourth clutch C1 and the
first and second brakes B1 and B2 are simultaneously operated.
Therefore, in a state in which the second rotating shaft TM2 is
connected to the sixth rotating shaft TM6 to each other by the
operation of the fourth clutch C4, the power is inputted to the
third rotating shaft TM3, while the first rotating shaft TM1 is
operated as a fixing element and simultaneously the fifth rotating
shaft TM5 and the eighth rotating shaft TM8 are operated as a
fixing element by the operation of the first brake B1 and the
second brake B2, the reverse speed is realized and the power is
output through the output shaft OS including the seventh rotating
shaft TM7.
[0074] The planetary gear train according to the exemplary
embodiment of the present invention may implement the gear shift
stages for nine forward speed stages and one reverse speed stage by
operating and controlling the four planetary gear sets PG1, PG2,
PG3, and PG4 using the four clutches C1, C2, C3, and C4 and the two
brakes B1 and B2.
[0075] In addition, the linearity of the interstage ratio of the
shift stage is secured while multi-staging the shift stage at high
efficiency, thereby making it possible to improve drivability such
as acceleration before and after the shift, an engine speed
rhythmic sense, and the like.
[0076] In addition, a span of a gear shift ratio is 9.0 or more,
thereby maximizing driving efficiency of the engine.
[0077] For convenience in explanation and accurate definition in
the appended claims, the terms "upper", "lower", "inner" and
"outer" are used to describe features of the exemplary embodiments
with reference to the positions of such features as displayed in
the figures.
[0078] 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.
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