U.S. patent application number 16/576033 was filed with the patent office on 2020-12-03 for power transmission apparatus for vehicle.
This patent application is currently assigned to Hyundai Motor Company. The applicant listed for this patent is Hyundai Motor Company, Kia Motors Corporation. Invention is credited to Minho Chae, Soonki Eo, Seong Wook Hwang, Chon Ok Kim, Sun Sung Kwon, Yong Uk Shin.
Application Number | 20200378485 16/576033 |
Document ID | / |
Family ID | 1000005218628 |
Filed Date | 2020-12-03 |
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United States Patent
Application |
20200378485 |
Kind Code |
A1 |
Kim; Chon Ok ; et
al. |
December 3, 2020 |
POWER TRANSMISSION APPARATUS FOR VEHICLE
Abstract
A transmission may include a first input shaft, a second input
shaft external and selectively connectable to the first input
shaft, a third input shaft external to the second input shaft and
selectively connectable to the first input shaft, an intermediate
shaft, an idle shaft, and an output shaft, a planetary gear set
mounted on the intermediate shaft and having first to third
elements where the third element and one the first and second
elements are selectively connectable to the intermediate shaft and
the first and second elements are connected to the third and second
input shafts, a plurality of gear sets allowing torque flows
between the various shafts and the planetary gear set, first and
second synchronizers on the output shaft, receiving torques from
the input shafts, and selectively transmitting the received torque
to the output shaft, and four clutches.
Inventors: |
Kim; Chon Ok; (Yongin-si,
KR) ; Hwang; Seong Wook; (Gunpo-si, KR) ; Eo;
Soonki; (Ansan-si, KR) ; Chae; Minho;
(Incheon, KR) ; Kwon; Sun Sung; (Anyang-si,
KR) ; Shin; Yong Uk; (Suwon-si, KR) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Hyundai Motor Company
Kia Motors Corporation |
Seoul
Seoul |
|
KR
KR |
|
|
Assignee: |
Hyundai Motor Company
Seoul
KR
Kia Motors Corporation
Seoul
KR
|
Family ID: |
1000005218628 |
Appl. No.: |
16/576033 |
Filed: |
September 19, 2019 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F16H 2200/0065 20130101;
F16H 2200/2005 20130101; F16H 37/046 20130101; F16H 57/08 20130101;
F16H 2037/048 20130101; F16H 2702/02 20130101 |
International
Class: |
F16H 37/04 20060101
F16H037/04; F16H 57/08 20060101 F16H057/08 |
Foreign Application Data
Date |
Code |
Application Number |
Jun 3, 2019 |
KR |
10-2019-0065338 |
Claims
1. A power transmission apparatus for a vehicle, the power
transmission apparatus comprising: a first input shaft fixedly
connected to an engine output shaft fixedly connected to an engine;
a second input shaft formed as a hollow shaft, mounted coaxial with
and external to the first input shaft without rotational
interference therebetween, and selectively connectable to the first
input shaft; a third input shaft formed as a hollow shaft, mounted
coaxial with and external to the second input shaft, and
selectively connectable to the first input shaft; an intermediate
shaft, an idle shaft, and at least one output shaft mounted in
parallel with the first, second, and third input shafts; a
planetary gear set having a first rotation element, a second
rotation element, and a third rotation element and mounted on an
axis of the intermediate shaft, wherein the third rotation element
and one of the first rotation element and the second rotation
element are selectively connectable to the intermediate shaft and
wherein the first rotation element and the second rotation element
are engaged to the third and second input shafts; a plurality of
gear sets, each of which allows at least one torque flow between
the intermediate shaft, the first, second, and third input shafts,
the idle shaft, the at least one output shaft, and the planetary
gear set; a first synchronizer mounted on the at least one output
shaft, selectively receiving a torque from the second input shaft
through two paths, and transmitting the received torque to the at
least one output shaft; a second synchronizer mounted on the at
least one output shaft, selectively receiving a torque from the
third input shaft through two paths, and transmitting the received
torque to the at least one output shaft; and four clutches.
2. The power transmission apparatus of claim 1, wherein the at
least one output shaft includes a first output shaft mounted in a
torque path between the second and third input shafts and a
differential.
3. The power transmission apparatus of claim 2, wherein the first
and third rotation elements of the planetary gear set are
selectively connectable to the intermediate shaft.
4. The power transmission apparatus of claim 3, wherein the four
clutches include: a first clutch mounted between the first input
shaft and the second input shaft; a second clutch mounted between
the first input shaft and the third input shaft; a third clutch
mounted between the intermediate shaft and the third rotation
element of the planetary gear set; and a fourth clutch mounted
between the intermediate shaft and the first rotation element of
the planetary gear set.
5. The power transmission apparatus of claim 2, wherein the second
and third rotation elements of the planetary gear set are
selectively connectable to the intermediate shaft.
6. The power transmission apparatus of claim 5, wherein the four
clutches include: a first clutch mounted between the first input
shaft and the second input shaft; a second clutch mounted between
the first input shaft and the third input shaft; a third clutch
mounted between the intermediate shaft and the third rotation
element of the planetary gear set; and a fourth clutch mounted
between the intermediate shaft and the second rotation element of
the planetary gear set.
7. The power transmission apparatus of claim 2, wherein the
plurality of gear sets includes: a first gear set including a first
input gear and a first gear, the first input gear being fixedly
connected to the first input shaft, the first gear being fixedly
connected to the intermediate shaft and gear-engaged with the first
input gear; a second gear set including a second input gear and a
first shifting gear, the second input gear being fixedly connected
to the second input shaft, the first shifting gear being rotatably
mounted on the first output shaft and gear-engaged with the second
input gear; a third gear set including a second gear, a third input
gear, and a second shifting gear, the second gear being fixedly
connected to the second rotation element of the planetary gear set,
the third input gear being fixedly connected to the second input
shaft and gear-engaged with the second gear, and the second
shifting gear being rotatably mounted on the first output shaft and
gear-engaged with the third input gear; a fourth gear set including
a fourth input gear, a third shifting gear, and an idle gear, the
fourth input gear being fixedly connected to the third input shaft,
the third shifting gear being rotatably mounted on the first output
shaft, the idle gear being fixedly connected to the idle shaft and
gear-engaged with the fourth input gear and the third shifting
gear; a fifth gear set including a third gear and a fourth gear,
the third gear being fixedly connected to the first rotation
element of the planetary gear set, the fourth gear being fixedly
connected to the third input shaft and gear-engaged with the third
gear; and a sixth gear set including a fifth input gear and a
fourth shifting gear, the fifth input gear being fixedly connected
to the third input shaft, the fourth shifting gear being rotatably
mounted on the first output shaft and gear-engaged with the fifth
input gear.
8. The power transmission apparatus of claim 7, wherein the
plurality of gear sets further include a seventh gear set including
a final reduction gear of a differential, and a first output gear
fixedly connected to the first output shaft and gear-engaged with
the final reduction gear.
9. The power transmission apparatus of claim 7, wherein the first,
second, third, fourth, fifth, and sixth gear sets are mounted in
series of the sixth, fifth, fourth, third, second, and first gear
sets from a side of the engine output shaft.
10. The power transmission apparatus of claim 7, wherein the first
synchronizer is configured to selectively connect one of the first
shifting gear of the second gear set and the second shifting gear
of the third gear set to the first output shaft, and wherein the
second synchronizer is configured to selectively connect one of the
third shifting gear of the fourth gear set and the fourth shifting
gear of the sixth gear set to the first output shaft.
11. The power transmission apparatus of claim 1, wherein the at
least one output shaft includes: a first output shaft mounted in a
torque path between the second input shaft and a differential; and
a second output shaft mounted in a torque path between the third
input shaft and the differential.
12. The power transmission apparatus of claim 11, wherein the first
and third rotation elements of the planetary gear set are
selectively connectable to the intermediate shaft.
13. The power transmission apparatus of claim 12, wherein the four
clutches include: a first clutch mounted between the first input
shaft and the second input shaft; a second clutch mounted between
the first input shaft and the third input shaft; a third clutch
mounted between the intermediate shaft and the third rotation
element of the planetary gear set; and a fourth clutch mounted
between the intermediate shaft and the first rotation element of
the planetary gear set.
14. The power transmission apparatus of claim 11, wherein the
second and third rotation elements of the planetary gear set are
selectively connectable to the intermediate shaft.
15. The power transmission apparatus of claim 14, wherein the four
clutches include: a first clutch mounted between the first input
shaft and the second input shaft; a second clutch mounted between
the first input shaft and the third input shaft; a third clutch
mounted between the intermediate shaft and the third rotation
element of the planetary gear set; and a fourth clutch mounted
between the intermediate shaft and the second rotation element of
the planetary gear set.
16. The power transmission apparatus of claim 11, wherein the
plurality of gear sets include: a first gear set including a first
input gear and a first gear, the first input gear being fixedly
connected to the first input shaft, the first gear being fixedly
connected to the intermediate shaft and gear-engaged with the first
input gear; a second gear set including a second input gear and a
first shifting gear, the second input gear being fixedly connected
to the second input shaft, the first shifting gear being rotatably
mounted on the first output shaft and gear-engaged with the second
input gear; a third gear set including a second gear, a third input
gear, and a second shifting gear, the second gear being fixedly
connected to the second rotation element of the planetary gear set,
the third input gear being fixedly connected to the second input
shaft and gear-engaged with the second gear, and the second
shifting gear being rotatably mounted on the first output shaft and
gear-engaged with the third input gear; a fourth gear set including
a fourth input gear, a third shifting gear, and an idle gear, the
fourth input gear being fixedly connected to the third input shaft,
the third shifting gear being rotatably mounted on the second
output shaft, and the idle gear fixedly connected to the idle shaft
and gear-engaged with the fourth input gear and the third shifting
gear; a fifth gear set including a third gear and a fourth gear,
the third gear being fixedly connected to the first rotation
element of the planetary gear set, the fourth gear being fixedly
connected to the third input shaft and gear-engaged with the third
gear; and a sixth gear set including a fifth input gear and a
fourth shifting gear, the fifth input gear being fixedly connected
to the third input shaft, the fourth shifting gear being rotatably
mounted on the second output shaft and gear-engaged with the fifth
input gear.
17. The power transmission apparatus of claim 16, wherein the
plurality of gear sets further include a seventh gear set that
includes a final reduction gear of a differential, and first and
second output gears, the first and second output gears being
fixedly connected to the first output shaft and the second output
shaft, respectively, and gear-engaged with the final reduction
gear.
18. The power transmission apparatus of claim 16, wherein the
first, second, third, fourth, fifth, and sixth gear sets are
mounted in series of the sixth, fifth, fourth, third, second and
first gear sets from a side of the engine output shaft.
19. The power transmission apparatus of claim 16, wherein the first
synchronizer is configured to selectively connect one of the first
shifting gear of the second gear set and the second shifting gear
of the third gear set to the first output shaft, and wherein the
second synchronizer is configured to selectively connect one of the
third shifting gear of the fourth gear set and the fourth shifting
gear of the sixth gear set to the second output shaft.
20. The power transmission apparatus of claim 1, wherein the
planetary gear set is a single pinion planetary gear set having a
sun gear, a planet carrier, and a ring gear as the first rotation
element, the second rotation element and the third rotation element
respectively.
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] The present application claims priority to Korean Patent
Application No. 10-2019-0065338 filed on Jun. 3, 2019, the entire
contents of which is incorporated herein for all purposes by this
reference.
BACKGROUND OF THE INVENTION
Field of the Invention
[0002] The present invention relates to a power transmission
apparatus for a vehicle.
Description of Related Art
[0003] Research on realizing more shifting stages of an automatic
transmission are undertaken to achieve enhancement of fuel
consumption and better drivability, and recently, increase of oil
price is triggering a hard competition in enhancing fuel
consumption of a vehicle.
[0004] In the present sense, research on an engine has been
undertaken to achieve weight reduction and to enhance fuel
consumption by so-called downsizing research on an automatic
transmission has been performed to simultaneously provide better
drivability and fuel consumption by achieving more shifting
stages.
[0005] To achieve more shifting stages for an automatic
transmission, the number of parts is typically increased, which may
deteriorate installability, production cost, weight and/or power
flow efficiency.
[0006] Therefore, to maximally enhance fuel consumption of an
automatic transmission having more shifting stages, it is important
for better efficiency to be derived by fewer number of parts.
[0007] In the present respect, an eight-speed automatic
transmission has been recently introduced, and a planetary gear
train for an automatic transmission facilitating more shifting
stages is under investigation.
[0008] An automatic transmission of eight or more shifting stages
typically may include three to four planetary gear sets and five to
seven engagement elements (friction elements), and may easily
become lengthy, deteriorating installability.
[0009] In this regard, disposing planetary gear sets in parallel or
employing dog clutches instead of wet-type control elements is
sometimes attempted. However, such an arrangement may not be widely
applicable, and using dog clutches may easily deteriorate
shift-feel.
[0010] The information included in this Background of the Invention
section is only for enhancement of understanding of the general
background of the invention and may 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
[0011] Various aspects of the present invention are directed to
providing a power transmission apparatus for a vehicle having
advantages of improvement of power delivery performance and fuel
consumption
[0012] An exemplary power transmission apparatus may include a
first input shaft fixedly connected to an engine output shaft, a
second input shaft formed as a hollow shaft, mounted coaxial with
and external to the first input shaft without rotational
interference therebetween, and selectively connectable to the first
input shaft, a third input shaft formed as a hollow shaft, mounted
coaxial with and external to the second input shaft, and
selectively connectable to the first input shaft, an intermediate
shaft, an idle shaft, and at least one output shaft mounted in
parallel with the first, second, and third input shafts, a
planetary gear set having first, second, and third rotation
elements and mounted on an axis of the intermediate shaft, the
third rotation element and one rotation element of the first and
second rotation elements being selectively connectable to the
intermediate shaft, the first and second rotation elements being
connected to the third and second input shafts, a plurality of gear
sets, each of which allows at least one torque flow between the
intermediate shaft, the first, second, and third input shafts, the
idle shaft, the output shaft, and the planetary gear set, a first
synchronizer mounted on the output shaft, selectively receiving a
torque from the second input shaft through two paths, and
transmitting the received torque to the output shaft, a second
synchronizer mounted on the output shaft, selectively receiving a
torque from the third input shaft through two paths, and
transmitting the received torque to the output shaft, and four
clutches each of which facilitating selective connection.
[0013] The at least one output shaft may include a first output
shaft mounted in a torque path between the second and third input
shafts and a differential.
[0014] The first and third rotation elements of the planetary gear
set are selectively connectable to the intermediate shaft. The four
clutches may include a first clutch mounted between the first input
shaft and the second input shaft, a second clutch mounted between
the first input shaft and the third input shaft, a third clutch
mounted between the intermediate shaft and the third rotation
element of the planetary gear set, and a fourth clutch mounted
between the intermediate shaft and the first rotation element of
the planetary gear set.
[0015] The second and third rotation elements of the planetary gear
set may be selectively connectable to the intermediate shaft. The
four clutches may include a first clutch mounted between the first
input shaft and the second input shaft, a second clutch mounted
between the first input shaft and the third input shaft, a third
clutch mounted between the intermediate shaft and the third
rotation element of the planetary gear set, and a fourth clutch
mounted between the intermediate shaft and the second rotation
element of the planetary gear set.
[0016] The plurality of gear sets may include first, second, third,
fourth, fifth, and sixth gear sets. The first gear set may include
a first input gear and a first external gear, the first input gear
being fixedly connected to the first input shaft, the first
external gear being fixedly connected to the intermediate shaft and
externally gear-meshed with the first input gear. The second gear
set may include a second input gear and a first shifting gear, the
second input gear being fixedly connected to the second input
shaft, the first shifting gear being rotatably mounted on the first
output shaft and externally gear-meshed with the second input gear.
The third gear set may include a second external gear, a third
input gear, and a second shifting gear, the second external gear
being fixedly connected to the second rotation element of the
planetary gear set, the third input gear being fixedly connected to
the second input shaft and externally gear-meshed with the second
external gear, and the second shifting gear being rotatably mounted
on the first output shaft and externally gear-meshed with the third
input gear. The fourth gear set may include a fourth input gear, a
third shifting gear, and an idle gear, the fourth input gear being
fixedly connected to the third input shaft, the third shifting gear
being rotatably mounted on the first output shaft, the idle gear
being fixedly connected to the idle shaft and externally
gear-meshed with the fourth input gear and the third shifting gear
respectively. The fifth gear set may include a third external gear
and a fourth external gear, the third external gear being fixedly
connected to the first rotation element of the planetary gear set,
the fourth external gear being fixedly connected to the third input
shaft and externally gear-meshed with the third external gear. The
sixth gear set may include a fifth input gear and a fourth shifting
gear, the fifth input gear being fixedly connected to the third
input shaft, the fourth shifting gear being rotatably mounted on
the first output shaft and externally gear-meshed with the fifth
input gear. The plurality of gear sets may further include a
seventh gear set including a final reduction gear of a
differential, and a first output gear fixedly connected to the
first output shaft and externally gear-meshed with the final
reduction gear.
[0017] The first, second, third, fourth, fifth, and sixth gear sets
may be mounted in a listed order from an opposite side of the
engine output shaft.
[0018] The first synchronizer may selectively connect the first
shifting gear of the second gear set and the second shifting gear
of the third gear set to the first output shaft. The second
synchronizer may selectively connect the third shifting gear of the
fourth gear set and the fourth shifting gear of the sixth gear set
to the first output shaft.
[0019] The at least one output shaft may include first and second
output shafts. The first output shaft may be mounted in a torque
path between the second input shaft and a differential. The second
output shaft may be mounted in a torque path between the third
input shaft and a differential.
[0020] The first and third rotation elements of the planetary gear
set may be selectively connectable to the intermediate shaft. The
four clutches may include a first clutch mounted between the first
input shaft and the second input shaft, a second clutch mounted
between the first input shaft and the third input shaft, a third
clutch mounted between the intermediate shaft and the third
rotation element of the planetary gear set, and a fourth clutch
mounted between the intermediate shaft and the first rotation
element of the planetary gear set.
[0021] The second and third rotation elements of the planetary gear
set may be selectively connectable to the intermediate shaft. The
four clutches may include a first clutch mounted between the first
input shaft and the second input shaft, a second clutch mounted
between the first input shaft and the third input shaft, a third
clutch mounted between the intermediate shaft and the third
rotation element of the planetary gear set, and a fourth clutch
mounted between the intermediate shaft and the second rotation
element of the planetary gear set.
[0022] The plurality of gear sets may include first, second, third,
fourth, fifth, and sixth gear sets. The first gear set may include
a first input gear and a first external gear, the first input gear
being fixedly connected to the first input shaft, the first
external gear being fixedly connected to the intermediate shaft and
externally gear-meshed with the first input gear. The second gear
set may include a second input gear and a first shifting gear, the
second input gear being fixedly connected to the second input
shaft, the first shifting gear being rotatably mounted on the first
output shaft and externally gear-meshed with the second input gear.
The third gear set may include a second external gear, a third
input gear, and a second shifting gear, the second external gear
being fixedly connected to the second rotation element of the
planetary gear set, the third input gear being fixedly connected to
the second input shaft and externally gear-meshed with the second
external gear, and the second shifting gear being rotatably mounted
on the first output shaft and externally gear-meshed with the third
input gear. The fourth gear set may include a fourth input gear, a
third shifting gear, and an idle gear, the fourth input gear being
fixedly connected to the third input shaft, the third shifting gear
being rotatably mounted on the second output shaft, and the idle
gear fixedly connected to the idle shaft and externally gear-meshed
with the fourth input gear and the third shifting gear
respectively. The fifth gear set may include a third external gear
and a fourth external gear, the third external gear being fixedly
connected to the first rotation element of the planetary gear set,
the fourth external gear being fixedly connected to the third input
shaft and externally gear-meshed with the third external gear. The
sixth gear set may include a fifth input gear and a fourth shifting
gear, the fifth input gear being fixedly connected to the third
input shaft, the fourth shifting gear being rotatably mounted on
the second output shaft and externally gear-meshed with the fifth
input gear. The plurality of gear sets may further include a
seventh gear set that may include a final reduction gear of a
differential, and first and second output gears, the first and
second output gears being fixedly connected to the first and second
output shafts and externally gear-meshed with the final reduction
gear.
[0023] The first, second, third, fourth, fifth, and sixth gear sets
may be mounted in a listed order from an opposite side of the
engine output shaft.
[0024] The first synchronizer may selectively connect the first
shifting gear of the second gear set and the second shifting gear
of the third gear set to the first output shaft. The second
synchronizer may selectively connect the third shifting gear of the
fourth gear set and the fourth shifting gear of the sixth gear set
to the second output shaft.
[0025] The planetary gear set may be a single pinion planetary gear
set having a sun gear, a planet carrier, and a ring gear as the
first, second, and third rotation elements respectively.
[0026] A power transmission apparatus configured for a vehicle
according to an exemplary embodiment of the present invention may
realize sixteen shifting stages by combining one simple planetary
gear set and two synchronizers to basic four-speed dual-clutch
transmission (DCT) structure.
[0027] Furthermore, according to a power transmission apparatus
configured for a vehicle according to an exemplary embodiment of
the present invention, desired shifting stages may be selected from
the sixteen shifting stages, and therefore, a transmission may be
easily optimized for various specifications of vehicles,
facilitating vehicle-specifically improvement of power delivery
performance and fuel consumption.
[0028] Furthermore, according to a power transmission apparatus
configured for a vehicle according to an exemplary embodiment of
the present invention, a transmission may be down-sized by
employing a simple four-speed dual-clutch transmission (DCT)
structure, also improving installability.
[0029] Furthermore, effects which may 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.
[0030] 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
[0031] FIG. 1 is a schematic view of a power transmission apparatus
configured for a vehicle according to various exemplary embodiments
of the present invention.
[0032] FIG. 2 is a shifting operation chart for a power
transmission apparatus configured for a vehicle according to
various exemplary embodiments of the present invention.
[0033] FIG. 3 is a schematic view of a power transmission apparatus
configured for a vehicle according to various exemplary embodiments
of the present invention.
[0034] FIG. 4 is a schematic view of a power transmission apparatus
configured for a vehicle according to various exemplary embodiments
of the present invention.
[0035] FIG. 5 is a schematic view of a power transmission apparatus
configured for a vehicle according to various exemplary embodiments
of the present invention.
[0036] It may 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 present invention. The specific design features
of the present invention as included herein, including, for
example, specific dimensions, orientations, locations, and shapes
will be determined in part by the particularly intended application
and use environment.
[0037] In the figures, reference numbers refer to the same or
equivalent portions of the present invention throughout the several
figures of the drawing.
DETAILED DESCRIPTION
[0038] 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 present
invention(s) will be described in conjunction with exemplary
embodiments of the present invention, it will be understood that
the present description is not intended to limit the present
invention(s) to those exemplary embodiments. On the other hand, the
present invention(s) is/are intended to cover not only the
exemplary embodiments of the present invention, but also various
alternatives, modifications, equivalents and other embodiments,
which may be included within the spirit and scope of the present
invention as defined by the appended claims.
[0039] In the following detailed description, only certain
exemplary embodiments of the present invention have been shown and
described, simply by way of illustration. 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.
[0040] The drawings and description are to be regarded as
illustrative in nature and not restrictive, and like reference
numerals designate like elements throughout the specification.
[0041] 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.
[0042] FIG. 1 is a schematic view of a power transmission apparatus
according to various exemplary embodiments of the present
invention.
[0043] Referring to FIG. 1, a power transmission apparatus
according to various exemplary embodiments of the present invention
includes first, second, and third input shafts IS1, IS2, and IS3,
an intermediate shaft CS, an idle shaft IDS, a first output shaft
OS1, a planetary gear set PG, first, second, third, fourth, fifth,
sixth, and seventh gear sets GT1, GT2, GT3, GT4, GT5, GT6, and GT7,
first and second synchronizers SM1 and SM2, and first, second,
third, and fourth clutches CL1, CL2, CL3, and CL4.
[0044] A power source of the power transmission apparatus may be
various types of a known engine ENG, such as a gasoline engine or a
diesel engine.
[0045] The first, second, and third input shafts IS1, IS2, and IS3
are disposed at a same axis.
[0046] The first input shaft IS1 is an input member, and fixedly
connected to an engine output shaft EOS (or a crankshaft) of an
engine ENG, and a first input gear IG1 is fixedly mounted on an
external circumference of the first input shaft IS1.
[0047] The first input shaft IS1 may receive the torque of the
engine output shaft EOS through a torque converter.
[0048] The second input shaft IS2 is formed as a hollow shaft,
mounted coaxial with and external to the first input shaft IS1
without rotational interference therebetween, and selectively
connectable to the first input shaft IS1.
[0049] The second input shaft IS2 is external to the first input
shaft IS1 excluding an end portion of the first input shaft IS1,
and second and third input gears IG2 and IG3 are fixedly mounted to
the second input shaft IS2 at locations toward the excluded end
portion of the first input shaft IS1.
[0050] The third input shaft IS3 is formed as a hollow shaft,
mounted coaxial with and external to the second input shaft IS2
without rotational interference therebetween, and selectively
connectable to the second input shaft IS2.
[0051] The third input shaft IS3 is external to the second input
shaft IS2 excluding an end portion of the second input shaft IS2,
and fourth and fifth input gears IG4 and IG5 are fixedly mounted to
the third input shaft IS3.
[0052] The intermediate shaft CS is mounted in parallel with the
first, second, and third input shafts IS1, IS2, and IS3, and is
fixedly mounted with a first external gear EG1 which is externally
gear-meshed with the first input gear IG1 at the first input shaft
IS1.
[0053] The first output shaft OS1 is an output element, and mounted
in parallel with the first, second, and third input shafts IS1,
IS2, and IS3. First, second, third, and fourth shifting gears SG1,
SG2, SG3, and SG4 are rotatably mounted on the first output shaft
OS1, and are externally gear-meshed with the second, third, fourth,
and fifth input gears IG2, IG3, IG4, and IG5 on the second and
third input shafts IS2 and IS3, respectively.
[0054] The first output shaft OS1 receives a shifted driving torque
through a plurality of gear sets and transmits the shifted driving
torque to a differential through a first output gear OG1 and a
final reduction gear FDG.
[0055] The fourth input gear IG4 and the third shifting gear SG3
are both externally gear-meshed with an idle gear IDG which is
fixedly connected to the idle shaft IDS.
[0056] The planetary gear set PG is mounted on an axis of the
intermediate shaft CS.
[0057] The planetary gear set PG merely outputs a torque received
from the first input shaft IS1, or outputs a shifted torque
obtained from torques from the first input shaft IS1 and the second
and third input shafts IS2 and IS3.
[0058] In more detail, the planetary gear set PG may receive
torques from the first input shaft IS1 and the second input shaft
IS2, outputting a shifted torque to the third input shaft IS3, or
may receive torques from the first input shaft IS1 and the third
input shaft IS3 thereby outputting a shifted torque to the second
input shaft IS2.
[0059] The planetary gear set PG is a single pinion planetary gear
set, and includes a sun gear S, a planet carrier PC rotatably
supporting a plurality of pinion gear P externally gear-meshed with
the sun gear S, and a ring gear R internally gear-meshed with the
plurality of pinion gear P engaged with the sun gear S. The sun
gear S acts as a first rotation element N1, the planet carrier PC
acts as a second rotation element N2, and the ring gear R acts as a
third rotation element N3.
[0060] The first and third rotation elements N1 and N3 are
selectively connectable to the intermediate shaft CS, respectively,
and the second and first rotation elements N2 and N1 are
respectively connected to the second and third input shafts IS2 and
IS3 through corresponding gear sets.
[0061] The seven gear sets GT1 to GT7 are hereinafter described in
detail.
[0062] The first gear set GT1 includes a first input gear IG1 and a
first external gear EG1. The first input gear IG1 is fixedly
connected to the first input shaft IS1, and the first external gear
EG1 is fixedly connected to the intermediate shaft CS and
externally gear-meshed with the first input gear IG1.
[0063] In the first gear set GT1 of various exemplary embodiments
of the present invention, the first external gear EG1 may be
selectively connectable to the first rotation element N1 (sun gear
S) and the third rotation element N3 (ring gear R) of the planetary
gear set PG, through the intermediate shaft CS.
[0064] The second gear set GT2 includes a second input gear IG2 and
a first shifting gear SG1. The second input gear IG2 is fixedly
connected to the second input shaft IS2, and the first shifting
gear SG1 rotatably mounted on the first output shaft OS1 and
externally gear-meshed with the second input gear IG2.
[0065] The third gear set GT3 includes a second external gear EG2,
the third input gear IG3, and the second shifting gear SG2. The
second external gear EG2 is fixedly connected to the second
rotation element N2 (planet carrier PC) of the planetary gear set
PG. The third input gear IG3 is fixedly connected to second input
shaft IS2 and externally gear-meshed with the second external gear
EG2. The second shifting gear SG2 is rotatably mounted on the first
output shaft OS1 and externally gear-meshed with the third input
gear IG3.
[0066] The fourth gear set GT4 includes the fourth input gear IG4,
the third shifting gear SG3, and an idle gear IDG. The fourth input
gear IG4 is fixedly connected to the third input shaft IS3. The
third shifting gear SG3 is rotatably mounted on the first output
shaft OS1. The idle gear IDG is fixedly connected to the idle shaft
IDS between the fourth input gear IG4 and the third shifting gear
SG3, and externally gear-meshed with the fourth input gear IG4 and
the third shifting gear SG3.
[0067] The fifth gear set GT5 includes a third external gear EG3
and a fourth external gear EG4. The third external gear EG3 is
fixedly connected to the first rotation element N1 (sun gear S) of
the planetary gear set PG. The fourth external gear EG4 is fixedly
connected to the third input shaft IS3 and externally gear-meshed
with the third external gear EG3.
[0068] The sixth gear set GT6 includes the fifth input gear IG5 and
the fourth shifting gear SG4. The fifth input gear IG5 is fixedly
connected to the third input shaft IS3. The fourth shifting gear
SG4 is rotatably mounted on the first output shaft OS1 and
externally gear-meshed with the fifth input gear IG5.
[0069] The seventh gear set GT7 includes a final reduction gear FDG
of the differential DIFF, and a first output gear OG1. The first
output gear OG1 is fixedly connected to the first output shaft OS1
and externally gear-meshed with the final reduction gear FDG.
[0070] The seven gear sets GT1 to GT7 are mounted in a sequence of
the first, second, third, fourth, fifth, sixth, and seventh gear
sets GT1, GT2, GT3, GT4, GT5, GT6, and GT7 from an opposite side of
the engine ENG.
[0071] The first, second, third, and fourth shifting gears SG1,
SG2, SG3, and SG4 rotatably mounted on the first output shaft OS1
are selectively connectable to the first output shaft OS1 by first
and second synchronizers SM1 and SM2.
[0072] The first synchronizer SM1 selectively synchronizes the
first shifting gear SG1 and the second shifting gear SG2 to the
first output shaft OS1, and the second synchronizer SM2 selectively
synchronizes the third shifting gear SG3 and the fourth shifting
gear SG4 to the first output shaft OS1.
[0073] The first and second synchronizers SM1 and SM2 may be formed
as a known scheme, and first and second sleeves SLE1 and SLE2
applied to the first and second synchronizers SM1 and SM2 may be
operated by actuators which may be controlled by a transmission
control unit.
[0074] Gear ratios of the first to seventh gear sets GT1 to GT7 may
be set in consideration of design requirements of a
transmission.
[0075] Furthermore, engagement elements of first to fourth clutches
CL1, CL2, CL3, and CL4 are mounted between rotation members such as
various shafts.
[0076] The four clutches CL1 to CL4 are mounted as follows.
[0077] The first clutch CL1 is mounted between the first input
shaft IS1 and the second input shaft IS2, and selectively connects
the first input shaft IS1 and the second input shaft IS2.
[0078] The second clutch CL2 is mounted between the first input
shaft IS1 and the third input shaft IS3, and selectively connects
the first input shaft IS1 and the third input shaft IS3.
[0079] The third clutch CL3 is mounted between the intermediate
shaft CS and the third rotation element N3 (ring gear R) of the
planetary gear set PG, and selectively connects the intermediate
shaft CS and the ring gear R.
[0080] The fourth clutch CL4 is mounted between the intermediate
shaft CS and the first rotation element N1 (sun gear S) of the
planetary gear set PG, and selectively connects the intermediate
shaft CS and the sun gear S.
[0081] The engagement elements of the first, second, third, and
fourth clutches C1, C2, C3, and C4 may be realized as multi-plate
hydraulic pressure friction devices that are frictionally engaged
by hydraulic pressure, however, it may not be understood to be
limited thereto, since various other configuration that are
electrically controllable may be available.
[0082] In the disclosure, when two or more members are described to
be "fixedly connected", where the member may be any of a shaft, an
input shaft, an output shaft, a rotation member, and a transmission
housing, it means that the fixedly connected members always rotate
at a same speed. That is, rotation elements and/or shafts fixedly
interconnected rotate in a same rotating direction and at a same
rotation speed.
[0083] When two or more members are described to be "selectively
connectable" by an engagement element, it means that the
selectively connectable members rotate separately when the
engagement element is not engaged, and rotates at a same speed when
the engagement element is engaged. It may be understood that in the
case that a member is "selectively connectable" with a transmission
housing by an engagement element, the member may be stationary when
the engagement element is engaged.
[0084] FIG. 2 is a shifting operation chart for a power
transmission apparatus according to various exemplary embodiments
of the present invention, and the power transmission apparatus
according to various exemplary embodiments performs shifting
operation as follows.
[0085] A power transmission apparatus according to various
exemplary embodiments may realize a plurality of shifting stages by
selection operation of the engagement elements of the four clutches
CL1 to CL4 and the two synchronizers SM1 and SM2.
[0086] The exemplary power transmission apparatus may realize
sixteen shifting stages that include two shifting stages by the
operation of the first synchronizer SM1 under the simultaneous
operation of the second and third clutches CL2 and CL3, two
shifting stages by the operation of the second synchronizer SM2
under the simultaneous operation of the first and third clutches
CL1 and CL3, two shifting stages by the operation of the first
synchronizer SM1 under the operation of the first clutch CL1, two
shifting stages by the operation of the second synchronizer SM2
under the operation of the second clutch CL2, four shifting stages
by the operation of the first synchronizer SM1 or second
synchronizer SM2 under the simultaneous operation of the third and
fourth clutches CL3 and CL4, and four shifting stages by the
operation of the first and second synchronizers SM1 and SM2 under
the operation of the third clutch CL3.
[0087] A power transmission apparatus according to various
exemplary embodiments may achieve a desired number of shifting
stages selected from the available sixteen shifting stages
depending on desired characteristic of a transmission.
[0088] When gear ratios of respective gear sets GT1 to GT7 and PG
are set as follows, gear ratios of the sixteen shifting stages may
be obtained as shown in FIG. 2.
[0089] For example, gear ratios of the respective gear sets GT1 to
GT6 and SPG may be formed as follows.
[0090] The gear ratio of the first external gear EG1 to the first
input gear EG1 in the first gear set GT1 may be 0.250.
[0091] The gear ratio of the first shifting gear SG1 to the second
input gear IG2 in the second gear set GT2 may be 2.500.
[0092] The gear ratio of the third input gear IG3 to the second
external gear EG2 in the third gear set GT3 may be 0.450.
[0093] The gear ratio of the second shifting gear SG2 to the third
input gear IG3 in the third gear set GT3 may be 0.724.
[0094] The gear ratio of the third shifting gear SG3 to the fourth
input gear IG4 in the fourth gear set GT4 may be -4.000.
[0095] The gear ratio of the third external gear EG3 to the fourth
external gear EG4 in the fifth gear set GT5 may be 0.400.
[0096] The gear ratio of the fourth shifting gear SG4 to the fifth
input gear IG5 in the sixth gear set GT6 may be 0.913.
[0097] The gear ratio of the final reduction gear FDG to the first
output gear OG1 in the seventh gear set GT7 may be 3.667.
[0098] The gear ratio of the planetary gear set PG may be
1.400.
[0099] [First Shift-Stage]
[0100] In the first shift-stage, while the second and third
clutches CL2 and CL3 are under operation, the first synchronizer
SM1 is controlled to synchronously connect the first shifting gear
SG1 and the first output shaft OS1.
[0101] As such, the torque of the engine ENG is input to the first
rotation element N1 of the planetary gear set PG by the operation
of the second clutch CL2 through the first input shaft IS1, the
second clutch CL2, the third input shaft IS3, and the fifth gear
set GT5, and simultaneously input to the third rotation element N3
of the planetary gear set PG by the operation of the third clutch
CL3 through the first input shaft IS1, the first gear set GT1, and
the third clutch CL3.
[0102] In the planetary gear set PG, the first rotation element N1
receives a torque according to the gear ratio of the fifth gear set
GT5, and the third rotation element N3 receives a torque according
to the gear ratio of the first gear set GT1.
[0103] The torques of the first and third input shafts IS1 and IS3
are shifted in the planetary gear set PG according to the rotation
speed difference of the first and third rotation elements N1 and N3
thereby outputting the shifted torque to the second rotation
element N2, and the torque of the second rotation element N2 is
shifted while passing through the third gear set GT3, the second
gear set GT2, the first output shaft OS1, the first output gear
OG1, and the final reduction gear FDG to be transmitted to the
differential DIFF.
[0104] In the first shift-stage, torques of the first and third
input shafts IS1 and IS3 are primarily shifted by the gear ratios
of the first and fifth gear sets GT1 and GT5 and by the rotation
speed difference of the first and third rotation elements N1 and N3
in the planetary gear set PG, and secondarily shifted by the gear
ratios of the third and second gear sets GT3 and GT2, afterwards
being transmitted to the first output shaft OS1.
[0105] In the instant case, the second synchronizer SM2 is
maintained to a neutral state, and the torque of the third input
shaft IS3 is not passed to the first output shaft OS1 through the
fifth gear set GT5 and the sixth gear set GT6.
[0106] [Second Shift-Stage]
[0107] In the second shift-stage, while the second and third
clutches CL2 and CL3 are under operation, the first synchronizer
SM1 is controlled to synchronously connect the second shifting gear
SG2 and the first output shaft OS1.
[0108] As such, the torque of the engine ENG is input to the first
rotation element N1 of the planetary gear set PG by the operation
of the second clutch CL2 through the first input shaft IS1, the
second clutch CL2, the third input shaft IS3, and the fifth gear
set GT5, and the fifth gear set GT5, and simultaneously input to
the third rotation element N3 of the planetary gear set PG by the
operation of the third clutch CL3 through the first input shaft
IS1, the first gear set GT1, and the third clutch CL3.
[0109] In the planetary gear set PG, the first rotation element N1
receives a torque according to the gear ratio of the fifth gear set
GT5, and the third rotation element N3 receives a torque according
to the gear ratio of the first gear set GT1.
[0110] The torques of the first and third input shafts IS1 and IS3
are shifted in the planetary gear set PG according to the rotation
speed difference of the first and third rotation elements N1 and N3
thereby outputting the shifted torque to the second rotation
element N2, and the torque of the second rotation element N2 is
shifted while passing through the third gear set GT3, the first
output shaft OS1, the first output gear OG1, and the final
reduction gear FDG to be transmitted to the differential DIFF.
[0111] In the first shift-stage, torques of the first and third
input shafts IS1 and IS3 are primarily shifted by the gear ratios
of the first and fifth gear sets GT1 and GT5 and by the rotation
speed difference of the first and third rotation elements N1 and N3
in the planetary gear set PG, and secondarily shifted by the gear
ratio of the third gear set GT3, afterwards being transmitted to
the first output shaft OS1.
[0112] In the instant case, the second synchronizer SM2 is
maintained to a neutral state, and the torque of the third input
shaft IS3 is not passed to the first output shaft OS1 through the
fifth gear set GT5 and the sixth gear set GT6.
[0113] [Third Shift-Stage]
[0114] In the third shift-stage, while the first and third clutches
CL1 and CL3 are under operation, the second synchronizer SM2 is
controlled to synchronously connect the third shifting gear SG3 and
the first output shaft OS1.
[0115] As such, the torque of the engine ENG is input to the second
rotation element N2 of the planetary gear set PG by the operation
of the first clutch CL1 through the first input shaft IS1, the
first clutch CL1, the second input shaft IS2, and the third gear
set GT3, and the fifth gear set GT5, and simultaneously input to
the third rotation element N3 of the planetary gear set PG by the
operation of the third clutch CL3 through the first input shaft
IS1, the first gear set GT1, and the third clutch CL3.
[0116] In the planetary gear set PG, the second rotation element N2
receives a torque according to the gear ratio of the third gear set
GT3, and the third rotation element N3 receives a torque according
to the gear ratio of the first gear set GT1.
[0117] The torques of the first and second input shafts IS1 and IS2
are shifted in the planetary gear set PG according to the rotation
speed difference of the second and third rotation elements N2 and
N3 thereby outputting the shifted torque to the first rotation
element N1, and the torque of the first rotation element N1 is
shifted while passing through the fifth gear set GT5, the fourth
gear set GT4, the first output shaft OS1, the first output gear
OG1, and the final reduction gear FDG to be transmitted to the
differential DIFF.
[0118] In the third shift-stage, torques of the first and second
input shafts IS1 and IS2 are primarily shifted by the gear ratios
of the first and third gear sets GT1 and GT3 and by the rotation
speed difference of the second and third rotation elements N2 and
N3 in the planetary gear set PG, and secondarily shifted by the
gear ratios of the fifth and fourth gear sets GT5 and GT4,
afterwards being transmitted to the first output shaft OS1.
[0119] In the instant case, the first synchronizer SM1 is
maintained to a neutral state, and the torque of the second input
shaft IS2 is not passed to the first output shaft OS1 through the
second gear set GT2 and the third gear set GT3.
[0120] [Fourth Shift-Stage]
[0121] In the fourth shift-stage, while the first and third
clutches CL1 and CL3 are under operation, the second synchronizer
SM2 is controlled to synchronously connect the fourth shifting gear
SG4 and the first output shaft OS1.
[0122] As such, the torque of the engine ENG is input to the second
rotation element N2 of the planetary gear set PG by the operation
of the first clutch CL1 through the first input shaft IS1, the
first clutch CL1, the second input shaft IS2, and the third gear
set GT3, and the fifth gear set GT5, and simultaneously input to
the third rotation element N3 of the planetary gear set PG by the
operation of the third clutch CL3 through the first input shaft
IS1, the first gear set GT1, and the third clutch CL3.
[0123] In the planetary gear set PG, the second rotation element N2
receives a torque according to the gear ratio of the third gear set
GT3, and the third rotation element N3 receives a torque according
to the gear ratio of the first gear set GT1.
[0124] The torques of the first and second input shafts IS1 and IS2
are shifted in the planetary gear set PG according to the rotation
speed difference of the second and third rotation elements N2 and
N3 thereby outputting the shifted torque to the first rotation
element N1, and the torque of the first rotation element N1 is
shifted while passing through the fifth gear set GT5, the sixth
gear set GT6, the first output shaft OS1, the first output gear
OG1, and the final reduction gear FDG to be transmitted to the
differential DIFF.
[0125] In the fourth shift-stage, torques of the first and second
input shafts IS1 and IS2 are primarily shifted by the gear ratios
of the first and third gear sets GT1 and GT3 and by the rotation
speed difference of the second and third rotation elements N2 and
N3 in the planetary gear set PG, and secondarily shifted by the
gear ratios of the fifth and sixth gear sets GT5 and GT6,
afterwards being transmitted to the first output shaft OS1.
[0126] In the instant case, the first synchronizer SM1 is
maintained to a neutral state, and the torque of the second input
shaft IS2 is not passed to the first output shaft OS1 through the
second gear set GT2 and the third gear set GT3.
[0127] [Fifth Shift-Stage]
[0128] In the fifth shift-stage, while the first clutch CL1 is
under operation, the first synchronizer SM1 is controlled to
synchronously connect the first shifting gear SG1 and the first
output shaft OS1.
[0129] As such, by the operation of the first clutch CL1, the
torque of the engine ENG is shifted while passing through the first
input shaft IS1, the first clutch CL1, the second input shaft IS2,
the second gear set GT2, the first output shaft OS1, the first
output gear OG1, and the final reduction gear FDG.
[0130] In the fifth shift-stage, the torque of the first input
shaft IS1 is shifted by the gear ratio of the second gear set GT2,
and transmitted to the first output shaft OS1.
[0131] In the instant case, the operation of the second
synchronizer SM2 to synchronously connect the third shifting gear
SG3 or fourth shifting gear SG4 to the first output shaft OS1 does
not affect the shifting operation.
[0132] [Sixth Shift-Stage]
[0133] In the sixth shift-stage, while the first clutch CL1 is
under operation, the first synchronizer SM1 is controlled to
synchronously connect the second shifting gear SG2 and the first
output shaft OS1.
[0134] As such, by the operation of the first clutch CL1, the
torque of the engine ENG is shifted while passing through the first
input shaft IS1, the first clutch CL1, the second input shaft IS2,
the third gear set GT4, the first output shaft OS1, the first
output gear OG1, and the final reduction gear FDG.
[0135] In the sixth shift-stage, the torque of the first input
shaft IS1 is shifted by the gear ratio of the third gear set GT4,
and transmitted to the first output shaft OS1.
[0136] In the instant case, the operation of the second
synchronizer SM2 to synchronously connect the third shifting gear
SG3 or fourth shifting gear SG4 to the first output shaft OS1 does
not affect the shifting operation.
[0137] [Seventh Shift-Stage]
[0138] In the seventh shift-stage, while the second clutch CL2 is
under operation, the second synchronizer SM2 is controlled to
synchronously connect the third shifting gear SG3 and the first
output shaft OS1.
[0139] As such, by the operation of the second clutch CL2, the
torque of the engine ENG is shifted while passing through the first
input shaft IS1, the second clutch CL2, the third input shaft IS3,
the fifth, the fourth gear set GT5 and GT4, the first output shaft
OS1, and the first output gear OG1, final reduction gear FDG.
[0140] In the seventh shift-stage, the torque of the first input
shaft IS1 is shifted by the gear ratio of the fifth and fourth gear
sets GT5 and GT4, and transmitted to the first output shaft
OS1.
[0141] In the instant case, the operation of the first synchronizer
SM1 to synchronously connect the first shifting gear SG1 or second
shifting gear SG2 to the first output shaft OS1 does not affect the
shifting operation.
[0142] [Eighth Shift-Stage]
[0143] In the eighth shift-stage, while the second clutch CL2 is
under operation, the second synchronizer SM2 is controlled to
synchronously connect the fourth shifting gear SG4 and the first
output shaft OS1.
[0144] As such, by the operation of the second clutch CL2, the
torque of the engine ENG is shifted while passing through the first
input shaft IS1, the second clutch CL2, the third input shaft IS3,
the sixth gear set GT6, the first output shaft OS1, the first
output gear OG1, and the final reduction gear FDG.
[0145] In the eighth shift-stage, the torque of the first input
shaft IS1 is shifted by the gear ratio of the sixth gear set GT6,
and transmitted to the first output shaft OS1.
[0146] In the instant case, the operation of the first synchronizer
SM1 to synchronously connect the first shifting gear SG1 or second
shifting gear SG2 to the first output shaft OS1 does not affect the
shifting operation.
[0147] [Ninth Shift-Stage]
[0148] In the ninth shift-stage, while the third and fourth
clutches CL3 and CL4 are under operation, the first synchronizer
SM1 is controlled to synchronously connect the first shifting gear
SG1 and the first output shaft OS1.
[0149] As such, the torque of the engine ENG is input to the third
rotation element N3 of the planetary gear set PG by the operation
of the third clutch CL3 through the first input shaft IS1, the
first gear set GT1, and the third clutch CL3, and simultaneously
input to the first rotation element N1 of the planetary gear set PG
by the operation of the fourth clutch CL4 through the first input
shaft IS1, the first gear set GT1, and the fourth clutch CL4.
[0150] As such, the planetary gear set PG integrally rotates by
receiving the same torque of the first input shaft IS1 through the
first and third rotation elements N1 and N3, and merely transmits
the torque of the first and third rotation elements N1 and N3 to
the first and second rotation elements N1 and N2.
[0151] The torque of the second rotation element N2 is shifted
while passing through the third gear set GT3, the second gear set
GT2, the first output shaft OS1, the first output gear OG1, and the
final reduction gear FDG to be transmitted to the differential
DIFF.
[0152] In the ninth shift-stage, the torque of the first input
shaft IS1 is shifted by the gear ratio of the first, third, and
second gear sets GT1, GT3, and GT2, and transmitted to the first
output shaft OS1.
[0153] Since the second synchronizer SM2 is maintained to a neutral
state, the torque output from the first rotation element N1 of the
planetary gear set PG is not transmitted to the first output shaft
OS1 and does not affect the shifting operation.
[0154] [Tenth Shift-Stage]
[0155] In the tenth shift-stage, while the third and fourth
clutches CL3 and CL4 are under operation, the first synchronizer
SM1 is controlled to synchronously connect the second shifting gear
SG2 and the first output shaft OS1.
[0156] As such, the torque of the engine ENG is input to the third
rotation element N3 of the planetary gear set PG by the operation
of the third clutch CL3 through the first input shaft IS1, the
first gear set GT1, and the third clutch CL3, and simultaneously
input to the first rotation element N1 of the planetary gear set PG
by the operation of the fourth clutch CL4 through the first input
shaft IS1, the first gear set GT1, and the fourth clutch CL4.
[0157] As such, the planetary gear set PG integrally rotates by
receiving the same torque of the first input shaft IS1 through the
first and third rotation elements N1 and N3, and merely transmits
the torque of the first and third rotation elements N1 and N3 to
the first and second rotation elements N1 and N2.
[0158] The torque of the second rotation element N2 is shifted
while passing through the third gear set GT3, the first output
shaft OS1, the first output gear OG1, and the final reduction gear
FDG to be transmitted to the differential DIFF.
[0159] In the tenth shift-stage, the torque of the first input
shaft IS1 is shifted by the gear ratios of the first gear set GT1
and the third gear set GT3, and transmitted to the first output
shaft OS1.
[0160] Since the second synchronizer SM2 is maintained to a neutral
state, the torque output from the first rotation element N1 of the
planetary gear set PG is not transmitted to the first output shaft
OS1 and does not affect the shifting operation.
[0161] [Eleventh Shift-Stage]
[0162] In the eleventh shift-stage, while the third and fourth
clutches CL3 and CL4 are under operation, the second synchronizer
SM2 is controlled to synchronously connect the third shifting gear
SG3 and the first output shaft OS1.
[0163] As such, the torque of the engine ENG is input to the third
rotation element N3 of the planetary gear set PG by the operation
of the third clutch CL3 through the first input shaft IS1, the
first gear set GT1, and the third clutch CL3, and simultaneously
input to the first rotation element N1 of the planetary gear set PG
by the operation of the fourth clutch CL4 through the first input
shaft IS1, the first gear set GT1, and the fourth clutch CL4.
[0164] As such, the planetary gear set PG integrally rotates by
receiving the same torque of the first input shaft IS1 through the
first and third rotation elements N1 and N3, and merely transmits
the torque of the first and third rotation elements N1 and N3 to
the first and second rotation elements N1 and N2.
[0165] The torque of the first rotation element N1 is shifted while
passing through the fifth and fourth gear sets GT5 and GT4, the
first output shaft OS1, the first output gear OG1, and the final
reduction gear FDG to be transmitted to the differential DIFF.
[0166] In the eleventh shift-stage, the torque of the first input
shaft IS1 is shifted by the gear ratios of the first, fifth, and
fourth gear sets GT1, GT5, and GT4, and transmitted to the first
output shaft OS1.
[0167] Since the first synchronizer SM1 is maintained to a neutral
state, the torque output from the second rotation element N2 of the
planetary gear set PG is not transmitted to the first output shaft
OS1 and does not affect the shifting operation.
[0168] [Twelfth Shift-Stage]
[0169] In the twelfth shift-stage, while the third and fourth
clutches CL3 and CL4 are under operation, the second synchronizer
SM2 is controlled to synchronously connect the fourth shifting gear
SG4 and the first output shaft OS1.
[0170] As such, the torque of the engine ENG is input to the third
rotation element N3 of the planetary gear set PG by the operation
of the third clutch CL3 through the first input shaft IS1, the
first gear set GT1, and the third clutch CL3, and simultaneously
input to the first rotation element N1 of the planetary gear set PG
by the operation of the fourth clutch CL4 through the first input
shaft IS1, the first gear set GT1, and the fourth clutch CL4.
[0171] As such, the planetary gear set PG integrally rotates by
receiving the same torque of the first input shaft IS1 through the
first and third rotation elements N1 and N3, and merely transmits
the torque of the first and third rotation elements N1 and N3 to
the first and second rotation elements N1 and N2.
[0172] The torque of the first rotation element N1 is shifted while
passing through the fifth gear set GT5, the sixth gear set GT6, the
first output shaft OS1, the first output gear OG1, and the final
reduction gear FDG to be transmitted to the differential DIFF.
[0173] In the twelfth shift-stage, the torque of the first input
shaft IS1 is shifted by the gear ratios of the first, fifth, and
sixth gear sets GT1, GT5, and GT6, and transmitted to the first
output shaft OS1.
[0174] Since the first synchronizer SM1 is maintained to a neutral
state, the torque output from the second rotation element N2 of the
planetary gear set PG is not transmitted to the first output shaft
OS1 and does not affect the shifting operation.
[0175] [Thirteenth Shift-Stage]
[0176] In the thirteenth shift-stage, while the third clutch CL3 is
under operation, the first synchronizer SM1 is controlled to
synchronously connect the first shifting gear SG1 and the first
output shaft OS1, and the second synchronizer SM2 is controlled to
synchronously connect the third shifting gear SG3 and the first
output shaft OS1.
[0177] As such, by the operation of the first synchronizer SM1, the
second rotation element N2 of the planetary gear set PG is
connected to the first output shaft OS1 through the third gear set
GT3 and the second gear set GT2, and by the operation of the second
synchronizer SM2, the first rotation element N1 of the planetary
gear set PG is connected to the first output shaft OS1 through the
fifth gear set GT5 and the fourth gear set GT4. in the instant
state, the torque of the engine ENG is input to the third rotation
element N3 of the planetary gear set PG through the first input
shaft IS1, the first gear set GT1, and the third clutch CL3.
[0178] As a result, the first and second rotation elements N1 and
N2 of the planetary gear set PG form a closed torque loop together
with the first output shaft OS1. In the instant case, the first
rotation element N1 receives a shifted torque according to the gear
ratios of the fifth and fourth gear sets GT5 and GT4, and the
second rotation element N2 receives a shifted torque according to
the gear ratios of the third and second gear sets GT3 and GT2.
Therefore, the torque input to the third rotation element N3 is
shifted and transmitted through the first output shaft OS1, the
first output gear OG1, and the final reduction gear FDG and to the
differential DIFF.
[0179] [Fourteenth Shift-Stage]
[0180] In the fourteenth shift-stage, while the third clutch CL3 is
under operation, the first synchronizer SM1 is controlled to
synchronously connect the first shifting gear SG1 and the first
output shaft OS1, and the second synchronizer SM2 is controlled to
synchronously connect the fourth shifting gear SG4 and the first
output shaft OS1.
[0181] As such, by the operation of the first synchronizer SM1, the
second rotation element N2 of the planetary gear set PG is
connected to the first output shaft OS1 through the third gear set
GT3 and the second gear set GT2, and by the operation of the second
synchronizer SM2, the first rotation element N1 of the planetary
gear set PG is connected to the first output shaft OS1 through the
fifth gear set GT5 and the sixth gear set GT6. in the instant
state, the torque of the engine ENG is input to the third rotation
element N3 of the planetary gear set PG through the first input
shaft IS1, the first gear set GT1, and the third clutch CL3.
[0182] As a result, the first and second rotation elements N1 and
N2 of the planetary gear set PG form a closed torque loop together
with the first output shaft OS1. In the instant case, the first
rotation element N1 receives a shifted torque according to the gear
ratios of the fifth and sixth gear sets GT5 and GT6, and the second
rotation element N2 receives a shifted torque according to the gear
ratios of the third and second gear sets GT3 and GT2. Therefore,
the torque input to the third rotation element N3 is shifted and
transmitted through the first output shaft OS1, the first output
gear OG1, and the final reduction gear FDG and to the differential
DIFF.
[0183] [Fifteenth Shift-Stage]
[0184] In the fifteenth shift-stage, while the third clutch CL3 is
under operation, the first synchronizer SM1 is controlled to
synchronously connect the second shifting gear SG2 and the first
output shaft OS1, and the second synchronizer SM2 is controlled to
synchronously connect the third shifting gear SG3 and the first
output shaft OS1.
[0185] As such, by the operation of the first synchronizer SM1, the
second rotation element N2 of the planetary gear set PG is
connected to the first output shaft OS1 through the third gear set
GT3, and by the operation of the second synchronizer SM2, the first
rotation element N1 of the planetary gear set PG is connected to
the first output shaft OS1 through the fifth gear set GT5 and the
fourth gear set GT4. in the instant state, the torque of the engine
ENG is input to the third rotation element N3 of the planetary gear
set PG through the first input shaft IS1, the first gear set GT1,
and the third clutch CL3.
[0186] As a result, the first and second rotation elements N1 and
N2 of the planetary gear set PG form a closed torque loop together
with the first output shaft OS1. In the instant case, the first
rotation element N1 receives a shifted torque according to the gear
ratios of the fifth and fourth gear sets GT5 and GT4, and the
second rotation element N2 receives a shifted torque according to
the gear ratios of the third gear set GT3. Therefore, the torque
input to the third rotation element N3 is shifted and transmitted
through the first output shaft OS1, the first output gear OG1, and
the final reduction gear FDG and to the differential DIFF.
[0187] [Sixteenth Shift-Stage]
[0188] In the sixteenth shift-stage, while the third clutch CL3 is
under operation, the first synchronizer SM1 is controlled to
synchronously connect the second shifting gear SG2 and the first
output shaft OS1, and the second synchronizer SM2 is controlled to
synchronously connect the fourth shifting gear SG4 and the first
output shaft OS1.
[0189] As such, by the operation of the first synchronizer SM1, the
second rotation element N2 of the planetary gear set PG is
connected to the first output shaft OS1 through the third gear set
GT3, and by the operation of the second synchronizer SM2, the first
rotation element N1 of the planetary gear set PG is connected to
the first output shaft OS1 through the fifth gear set GT5 and the
sixth gear set GT6. in the instant state, the torque of the engine
ENG is input to the third rotation element N3 of the planetary gear
set PG through the first input shaft IS1, the first gear set GT1,
and the third clutch CL3.
[0190] As a result, the first and second rotation elements N1 and
N2 of the planetary gear set PG form a closed torque loop together
with the first output shaft OS1. In the instant case, the first
rotation element N1 receives a shifted torque according to the gear
ratios of the fifth and sixth gear sets GT5 and GT6, and the second
rotation element N2 receives a shifted torque according to the gear
ratios of the third gear set GT3. Therefore, the torque input to
the third rotation element N3 is shifted and transmitted through
the first output shaft OS1, the first output gear OG1, and the
final reduction gear FDG and to the differential DIFF.
[0191] As a result, a transmission of desired number of shifting
stages with desired gear ratio may be designed with reference to
the gear ratios of the sixteen shifting stages. For example, as
shown in FIG. 2, a transmission of forward nine speeds and one
reverse speed may be designed using first, second, fifth, sixth,
seventh, eighth, ninth, tenth, thirteenth, and sixteenth shifting
stages.
[0192] FIG. 3 is a schematic view of a power transmission apparatus
according to various exemplary embodiments of the present
invention.
[0193] Referring to FIG. 3, in various exemplary embodiments of the
present invention, the fourth clutch CL4 is mounted between the
intermediate shaft CS and the second rotation element N2 (planet
carrier PC) of the planetary gear set PG, in comparison with the
various exemplary embodiments where the fourth clutch CL4 is
mounted between the intermediate shaft CS and the first rotation
element N1 (sun gear S) of the planetary gear set PG in FIG. 1.
[0194] The various exemplary embodiments only differ from the
various exemplary embodiments in the location of the fourth clutch
CL4, providing the same shafting operation and effect, which is
therefore not described in further detail.
[0195] FIG. 4 is a schematic view of a power transmission apparatus
according to various exemplary embodiments of the present
invention.
[0196] Referring to FIG. 4, in various exemplary embodiments in
comparison with the various exemplary embodiments of the present
invention in FIG. 1, the first output shaft OS1 is split into first
and second output shafts OS1 and OS2, where the first synchronizer
SM1 is mounted on the first output shaft OS1, and the second
synchronizer SM2 is mounted on the second output shaft OS2.
[0197] Therefore, the first output shaft OS1 may transmit a torque
from the second and third gear sets GT2 and GT3 to the differential
DIFF through the first output gear OG1 and the final reduction gear
FDG in the seventh gear set GT7. The second output shaft OS2 may
transmit a torque from the fourth, sixth gear set GT4 and GT6 to
the differential DIFF through the second output gear OG2 and the
final reduction gear FDG in the seventh gear set GT7.
[0198] As a result, final reduction gear ratio may be differently
designed from the various exemplary embodiments by the first and
second output gears OS1 and OS2.
[0199] FIG. 5 is a schematic view of a power transmission apparatus
according to various exemplary embodiments of the present
invention.
[0200] Referring to FIG. 5, in various exemplary embodiments of the
present invention, the fourth clutch CL4 is mounted between the
intermediate shaft CS and the second rotation element N2 (planet
carrier PC) of the planetary gear set PG, in comparison with the
various exemplary embodiments where the fourth clutch CL4 is
mounted between the intermediate shaft CS and the first rotation
element N1 (sun gear S) of the planetary gear set PG in FIG. 4.
[0201] The various exemplary embodiments only differ from the
various exemplary embodiments in the location of the fourth clutch
CL4, providing the same shafting operation and effect, which is
therefore not described in further detail.
[0202] As described above, a power transmission apparatus for a
vehicle according to an exemplary embodiment of the present
invention may realize sixteen shifting stages by combining one
simple planetary gear set and two synchronizers to basic four-speed
dual-clutch transmission (DCT) structure.
[0203] Furthermore, according to a power transmission apparatus for
a vehicle according to an exemplary embodiment of the present
invention, desired shifting stages may be selected from the sixteen
shifting stages, and therefore, a transmission may be easily
optimized for various specifications of vehicles, facilitating
vehicle-specifically improvement of power delivery performance and
fuel consumption.
[0204] Furthermore, according to a power transmission apparatus for
a vehicle according to an exemplary embodiment of the present
invention, a transmission may be down-sized by employing a simple
four-speed dual-clutch transmission (DCT) structure, also improving
installability.
[0205] For convenience in explanation and accurate definition in
the appended claims, the terms "upper", "lower", "inner", "outer",
"up", "down", "upwards", "downwards", "front", "rear", "back",
"inside", "outside", "inwardly", "outwardly", "internal",
"external", "inner", "outer", "forwards", and "backwards" are used
to describe features of the exemplary embodiments with reference to
the positions of such features as displayed in the figures. It will
be further understood that the term "connect" or its derivatives
refer both to direct and indirect connection.
[0206] 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 present 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 to explain certain principles of the
present invention and their practical application, to 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 present invention be defined by the Claims appended
hereto and their equivalents.
* * * * *