KR101637512B1 - Gear actuator of Dual clutch transmission - Google Patents

Gear actuator of Dual clutch transmission Download PDF

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Publication number
KR101637512B1
KR101637512B1 KR1020150041024A KR20150041024A KR101637512B1 KR 101637512 B1 KR101637512 B1 KR 101637512B1 KR 1020150041024 A KR1020150041024 A KR 1020150041024A KR 20150041024 A KR20150041024 A KR 20150041024A KR 101637512 B1 KR101637512 B1 KR 101637512B1
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KR
South Korea
Prior art keywords
gear
camshaft
worm wheel
cams
worm
Prior art date
Application number
KR1020150041024A
Other languages
Korean (ko)
Inventor
윤주호
이원호
이국선
신순철
Original Assignee
한국파워트레인 주식회사
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Publication date
Application filed by 한국파워트레인 주식회사 filed Critical 한국파워트레인 주식회사
Priority to KR1020150041024A priority Critical patent/KR101637512B1/en
Application granted granted Critical
Publication of KR101637512B1 publication Critical patent/KR101637512B1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • F16H1/163—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel with balls between the co-operating parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • F16H1/166—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel with members rotating around axes on the worm or worm-wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
    • F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
    • F16H61/688—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
    • F16H63/16—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism
    • F16H63/18—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism the final actuating mechanism comprising cams
    • F16H2003/093—

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear-Shifting Mechanisms (AREA)

Abstract

The present invention provides a gear actuator of a dual clutch transmission, which is used to operate a dual clutch transmission. The gear actuator of a dual clutch transmission comprises: a worm gear installed on a shaft of a motor; a first worm wheel gear engaged with the worm gear; a first one-way clutch bearing installed on the first worm wheel gear to be rotated in only one direction; a second worm wheel gear engaged with the first worm wheel gear; a second one-way clutch bearing installed on the second worm wheel gear to be rotated in only a direction opposite to the first one-way clutch bearing; a first gear installed on an equal shaft of the first worm wheel gear; a first cam shaft coupled to an equal shaft of the first gear and having a plurality of cams formed on the outer circumferential surface thereof; a second gear engaged with the first gear; a second cam shaft coupled to an equal shaft of the second gear and having a plurality of cams formed on the outer circumferential surface thereof; a third gear installed on an equal shaft of the second worm wheel gear; a third cam shaft coupled to an equal shaft of the third gear and having a plurality of cams formed on the outer circumferential surface thereof; a fourth gear engaged with a third gear to be rotated; and a fourth cam shaft coupled to an equal shaft of a fourth gear and having a plurality of cams formed on the outer circumferential surface thereof.

Description

Technical Field [0001] The present invention relates to a dual clutch transmission,

The present invention relates to a drive device for a dual clutch transmission used for operating a dual clutch transmission.

Generally, the dual clutch transmission (DCT) has advantages such as a manual transmission, less power loss, easy operation, and quick shift time. In this dual clutch transmission, for example, when the vehicle travels in the first stage which is the hole means, the second stage, which is the even means, is already waiting in a state in which the shifting is possible. In this state, the power of the hole means is shut off, . Due to these characteristics, the dual clutch transmission has a faster shift time and a shorter shift time than the manual transmission.

However, the driving apparatus for operating such a dual clutch transmission has a complicated structure and a large number of driving sources, resulting in an increase in the number of assembling operations and an increase in manufacturing cost. In addition, the conventional dual clutch transmission has a problem in that the degree of freedom of design is low because the expansion speed of the speed change stages is not easy.

Korean Registered Patent No. 10-1339895 (registered on December 03, 2014)

SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a dual clutch transmission that can reduce the number of driving sources used to operate a dual clutch transmission and simplify a driving mechanism, And to provide a driving apparatus for the same.

It is a further object of the present invention to provide a drive system for a dual clutch transmission that employs a mechanical structure to minimize control when changing the number of stages of the transmission to reduce the failure rate due to control errors.

It is still another object of the present invention to provide a driving apparatus for a dual clutch transmission that is operated only by a single driving motor to minimize noise and is suitable for a hybrid vehicle.

It is still another object of the present invention to provide a driving apparatus for a dual clutch transmission that can be easily expanded as the number of stages of a transmission increases.

In order to achieve the above object, the present invention provides a worm gear device comprising a motor, a worm gear provided on a shaft of the motor, a first worm wheel gear meshed with the worm gear, Way clutch bearing, a second worm wheel gear meshing with the first worm wheel gear, a second one-way clutch bearing provided on the second worm wheel gear and rotating only in a direction opposite to the first one-way clutch bearing, A first gear provided on the same shaft as the first worm wheel gear, a first cam shaft coupled to the same shaft as the first gear and provided with a plurality of cams on the outer circumferential surface, a second gear rotatably engaged with the first gear, A second camshaft coupled to the same shaft as the gear and provided with a plurality of cams on the outer circumferential surface thereof, a third gear provided on the same shaft as the second worm wheel gear, a second gear coupled to the same shaft as the third gear, A third camshaft provided with a cam, a fourth gear rotated by engagement with the third gear, and a fourth camshaft coupled to the same shaft as the fourth gear and provided with a plurality of cams on the outer circumferential surface thereof Driving device.

Wherein the first gear and the second gear are arranged such that their axes are aligned with each other and meshed with each other, a first shift fork is disposed between the first camshaft and the second camshaft, and the first camshaft and the second camshaft It is preferable that the first shift fork is moved by the cams.

Wherein the third gear and the fourth gear are disposed so that their axes are aligned with each other and meshed with each other, a second shift fork is disposed between the third camshaft and the fourth camshaft, and the third camshaft and the fourth gear are provided on the third camshaft and the third camshaft It is preferable that the second shift fork is moved by the cams.

The embodiment of the present invention has the effect of reducing the manufacturing cost as well as reducing the noise by simplifying the motor as a driving source used for operating the dual clutch transmission.

 Further, the present invention adopts a structure that can move the shift fork by a mechanical structure such as a cam, so that control can be minimized when the number of stages of the transmission is changed, thereby reducing the failure occurrence rate due to control errors and increasing the stability.

In addition, the present invention has an advantage in that it can be applied to various types of vehicles by providing a structure suitable for a hybrid vehicle or the like by minimizing noise by reducing the driving source to one.

Further, according to the present invention, even if only a part of the structure is changed by adding a camshaft, it can be easily expanded and applied according to the increase of the number of stages of the transmission, thereby increasing the degree of freedom of design.

1 is a perspective view illustrating a driving apparatus of a dual clutch transmission for explaining an embodiment of the present invention.
Fig. 2 is a perspective view of the driving apparatus of the dual clutch transmission shown in Fig. 1 as seen from the rear side. Fig.
3 is a plan view of Fig.
4 is a front view of Fig.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings so that those skilled in the art can easily carry out the present invention. The present invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. In order to clearly illustrate the present invention, parts not related to the description are omitted, and the same or similar components are denoted by the same reference numerals throughout the specification.

FIG. 1 is a perspective view for explaining an embodiment of the present invention, FIG. 2 is a perspective view of FIG. 1 viewed from the rear side, FIG. 3 is a plan view of FIG. 1, and FIG. 4 is a front view of FIG. Fig.

A driving device for a dual clutch transmission according to an embodiment of the present invention includes a motor 1, a worm gear 3, a first worm wheel 5, a first one-way clutch bearing 7, a second worm wheel 9, Way clutch bearing 11, a first gear 13, a first camshaft 15, a second gear 17, a second camshaft 19, a third gear 21, a third camshaft 23, A fourth gear 25, and a fourth camshaft 27. As shown in Fig.

In the embodiment of the present invention, only one motor 1 is used and can be controlled in forward and reverse directions by a control unit (not shown). The worm gear 3 can be coupled to the shaft of the motor 1. [

The first worm wheel gear 5 and the second worm wheel gear 9 are engaged with the worm gear 3 and can be rotated by driving the worm gear 3. The first worm wheel gear 5 and the second worm wheel gear 9 can be arranged to face each other with the worm gear 3 therebetween.

The first worm wheel gear (5) is provided with a first one-way clutch bearing (7) which rotates only in one direction. The second one-way clutch bearing 11 is also provided on the second worm wheel 9 so as to rotate only in one direction. It is preferable that the first one-way clutch bearing 7 and the second one-way clutch bearing 11 are arranged so as to rotate only in the directions opposite to each other. That is, the first one-way clutch bearing 7 and the second one-way clutch bearing 11 do not rotate the second worm wheel gear 9 when the first worm wheel gear 5 rotates, 9, the first worm wheel 5 does not rotate.

The first gear 13 is coupled to the same shaft as the first worm wheel 5 and can rotate together with the first worm wheel 5. The first camshaft 15 may also be coupled to the same shaft as the first gear 13 and rotated together with the first gear 13.

The first camshaft 15 is provided with a plurality of cams 15a on its outer circumferential surface. This cam 15a serves to move a first shift fork 29 to be described later.

The second gear 17 is engaged with the first gear 13 and can rotate in a direction opposite to the first gear 13. The first gear 13 and the second gear 17 may be spur gears. And the second camshaft 19 can be coupled to the second gear 17 on the same axis. Therefore, the second camshaft 19 can rotate together with the second gear 17 as it rotates. A plurality of other cams 19a can be coupled to the second camshaft 19. The first shift fork 29 for selecting the number of gears of the transmission (not shown) can change the number of gears of the hole means, for example. The first shift fork 29 can be disposed between the first camshaft 15 and the second camshaft 19 with the lug L portion. Therefore, it can move in the y-axis direction or the -y-axis direction by the cams 15a, 19a provided on the first camshaft 15 and the second camshaft 19 (refer to Fig. 1). The cams 15a and 19a provided on the first camshaft 15 and the second camshaft 19 can be adjusted in their positions and sizes according to the optimized design so that the movement amount and the moving direction of the first shift fork 29 can be adjusted have.

In the embodiment of the present invention, the first gear 13 and the second gear 17 are arranged such that their axes are parallel to each other. The first gear 13 and the second gear 17 may be engaged with each other and disposed in opposite directions.

The third gear 21 is coupled to the same shaft as the second worm wheel gear 9 and can rotate together with the second worm wheel 9. Also, the third camshaft 23 may be coupled to the same shaft as the third gear 21 and rotated together with the third gear 21.

The third camshaft 23 is provided with another plurality of cams 23a on its outer circumferential surface. The cam 23a serves to move the second shift fork 31 described later.

The fourth gear 25 is engaged with the third gear 21 and can rotate in the direction opposite to the third gear 21. The third gear 21 and the fourth gear 25 may be made of a spur gear. The fourth gear 25 may be coupled to the fourth camshaft 27 on the same axis. Therefore, the fourth camshaft 27 can rotate together as the fourth gear 25 rotates. A plurality of further cams 27a may be coupled to the fourth camshaft 27. [ The second shift fork 31 for selecting the number of gears of the transmission (not shown) can change the speed change stage of the even-numbered means, for example. The second shift fork 31 may be disposed between the third camshaft 23 and the fourth camshaft 27 with the lug L portion. Therefore, it can move in the y-axis direction or the -y-axis direction by the cams 23a and 27a provided on the third camshaft 23 and the fourth camshaft 27 (refer to Fig. 1). The cams 23a and 27a provided on the third camshaft 23 and the fourth camshaft 27 are adjusted in their positions and sizes according to the optimized design to adjust the movement amount and the moving direction of the second shift fork 31 .

The third gear 21 and the fourth gear 25 are arranged such that their axes are parallel to each other. The third gear 21 and the fourth gear 25 are engaged with each other and can rotate in opposite directions.

Since the first gear 13, the second gear 17, the third gear 21 and the fourth gear 25 are arranged in a line with each other in the embodiment of the present invention, the first camshaft 15, The camshaft 19, the third camshaft 23, and the fourth camshaft 27 are also arranged in a line.

Meanwhile, the second gear 17 and the fourth gear 25 are provided with a plurality of holes H along a predetermined radius with respect to the center of rotation. A ball portion of a locking ball (LB) can be inserted into the hole (see FIGS. 2 and 3). The locking ball LB serves to prevent the first gear 13, the second gear 17, the third gear 21 and the fourth gear 25 from being arbitrarily rotated by vibration and impact. This embodiment of the present invention prevents the gears from being arbitrarily rotated by vibration even when the first one-way clutch bearing 7 and the second one-way clutch bearing 11 are installed so as to rotate in opposite directions to each other, Can be secured.

The operation of the embodiment of the present invention will now be described.

First, a control unit (not shown) controls the motor 1 to rotate forward when the first shift fork 29 (for example, described later) for changing the hole means is to be moved. Then, the first worm wheel 5 rotates while the motor 1 is rotating forward. At this time, the second worm wheel 9 does not rotate by the operation of the second one-way clutch bearing 11. [ Then, the first worm wheel 5 rotates and the first gear 13 rotates, and the second gear 17 rotates in the direction opposite to the rotation direction of the first gear 13. At the same time, the first camshaft 15 rotates in the same direction as the first gear 13 and the second camshaft 19 rotates in the opposite direction to the first camshaft 15. At this time, the first shift fork 29 moves in the y direction or the -y direction by the cams 15a, 19a disposed on the outer peripheral side of the first camshaft 15 and the second camshaft 19. [

When a second shift fork 31 (for example, described later) is to be shifted, the control unit (not shown) controls the motor 1 to rotate forward.

Then, the second worm wheel 9 rotates while the motor 1 is rotating forward. At this time, the first worm wheel 5 does not rotate due to the operation of the first one-way clutch bearing 7. Then, the second worm wheel 9 rotates, the third gear 21 rotates, and the fourth gear 25 rotates in the direction opposite to the rotation direction of the third gear 21. At the same time, the third camshaft 23 rotates in the same direction as the third gear 21, and the fourth camshaft 27 rotates in the direction opposite to the third camshaft 23. [ At this time, the second shift fork 31 is moved in the y direction or the -y direction by the cams 23a, 27a disposed on the outer peripheral side of the third camshaft 23 and the fourth camshaft 27.

Accordingly, the first shift fork 29 and the second shift fork 31 can be moved and the number of stages of the transmission can be changed. The process of shifting the transmission by the movement of the first shift fork 29 and the second shift fork 31 is the same as the operation of a general dual clutch transmission, and thus a detailed description thereof will be omitted.

The present invention simplifies the motor as a drive source used for operating the dual clutch transmission, thereby reducing noise and manufacturing cost.

Further, the present invention adopts a structure that can move the shift fork by a mechanical structure such as a cam, so that when the number of stages of the transmission is changed, control is minimized, thereby reducing the failure occurrence rate due to control errors, .

Further, according to the present invention, even if only a part of the structure is changed by adding a camshaft, it can be easily expanded and applied according to an increase in the number of stages of the transmission, thereby increasing the degree of design freedom.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is to be understood that the invention is not limited to the disclosed exemplary embodiments, but, on the contrary, And it goes without saying that the invention belongs to the scope of the invention.

1. Motor,
3. Worm gear,
5. The first worm wheel gear,
7. First one-way clutch bearings,
9. The second worm wheel gear,
11. Second one-way clutch bearing
13. First gear,
15. First camshaft, 15a. cam,
17. Second gear,
19. Second camshaft, 19a. cam,
21. Third gear,
23. Third camshaft, 23a. cam,
25. The fourth gear,
27. Fourth camshaft, 27a. cam,
29. First shift fork,
31. Second shift fork

Claims (4)

motor,
A worm gear provided on an axis of the motor,
A first worm wheel gear engaged with the worm gear,
A first one-way clutch bearing which is provided in the first worm wheel gear and rotates only in one direction,
A second worm wheel gear engaged with the worm gear,
A second one-way clutch bearing provided in the second worm wheel gear and rotating only in a direction opposite to the first one-way clutch bearing,
A first gear provided on the same axis as the first worm wheel gear,
A first camshaft coupled to the same shaft as the first gear and having a plurality of cams on an outer circumferential surface thereof,
A second gear rotatably engaged with the first gear,
A second camshaft coupled to the same shaft as the second gear and having a plurality of cams provided on an outer circumferential surface thereof,
A third gear provided on the same axis as the second worm wheel gear,
A third camshaft coupled to the same axis as the third gear and having a plurality of cams provided on an outer circumferential surface thereof,
A fourth gear that meshes with the third gear and rotates,
And a fourth cam shaft coupled to the same shaft as the fourth gear and having a plurality of cams provided on an outer circumferential surface thereof,
Wherein the first gear and the second gear are arranged such that their axes are aligned with each other and meshed with each other, a first shift fork is disposed between the first camshaft and the second camshaft, and the first camshaft and the second camshaft And the first shift fork is moved by the cams. delete The method according to claim 1,
Wherein the third gear and the fourth gear are disposed so that their axes are aligned with each other and meshed with each other, a second shift fork is disposed between the third camshaft and the fourth camshaft, and the third camshaft and the fourth gear are provided on the third camshaft and the third camshaft And the second shift fork is moved by the cams. The method according to claim 1,
The second gear and the fourth gear
A hole is provided at an interval on one side thereof,
Wherein a locking ball is provided on one side of the second gear and the fourth gear, and a ball of the locking ball is inserted into the hole.
KR1020150041024A 2015-03-24 2015-03-24 Gear actuator of Dual clutch transmission KR101637512B1 (en)

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Application Number Priority Date Filing Date Title
KR1020150041024A KR101637512B1 (en) 2015-03-24 2015-03-24 Gear actuator of Dual clutch transmission

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KR1020150041024A KR101637512B1 (en) 2015-03-24 2015-03-24 Gear actuator of Dual clutch transmission

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KR101637512B1 true KR101637512B1 (en) 2016-07-07

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101103969B1 (en) * 2009-07-20 2012-01-06 현대자동차주식회사 Clutch Actuating Apparatus for Double Clutch Transmission
KR20120017740A (en) * 2010-08-19 2012-02-29 현대모비스 주식회사 Shifting apparatus for dual clutch transmission
KR20120050203A (en) * 2010-11-10 2012-05-18 현대자동차주식회사 Shifting apparatus for vehicle
US8596152B2 (en) * 2010-06-03 2013-12-03 C.R.F. Societa' Consortile Per Azioni Rotary drum for a gear control device for a motor-vehicle gearbox and a gear control device for a motor-vehicle gearbox having such a drum
KR101339895B1 (en) 2012-05-29 2013-12-10 (주) 솔텍 Shift apparatus of dual clutch transmission mechanism

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101103969B1 (en) * 2009-07-20 2012-01-06 현대자동차주식회사 Clutch Actuating Apparatus for Double Clutch Transmission
US8596152B2 (en) * 2010-06-03 2013-12-03 C.R.F. Societa' Consortile Per Azioni Rotary drum for a gear control device for a motor-vehicle gearbox and a gear control device for a motor-vehicle gearbox having such a drum
KR20120017740A (en) * 2010-08-19 2012-02-29 현대모비스 주식회사 Shifting apparatus for dual clutch transmission
KR20120050203A (en) * 2010-11-10 2012-05-18 현대자동차주식회사 Shifting apparatus for vehicle
KR101339895B1 (en) 2012-05-29 2013-12-10 (주) 솔텍 Shift apparatus of dual clutch transmission mechanism

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