KR20140067489A - Shifting apparatus for dual clutch transmission - Google Patents

Abstract

Disclosed is a dual-clutch transmission with a simplified structure for readily changing speed. The dual-clutch transmission for changing speed by displacing a synchronizer in a dual-clutch including a first countershaft and a second countershaft comprises: a first shift-fork unit for performing a shift operation by displacing a synchronizer adjacent to the first countershaft; a second shift-fork unit for performing a shift operation by displacing a synchronizer adjacent to the second countershaft; a drive motor for supplying driving force to drive the first and the second shift-fork unit; and a switch part for selectively transferring the driving force of the drive motor to one of the first and the second shift-fork unit.

Description

[0001] SHIFTING APPARATUS FOR DUAL CLUTCH TRANSMISSION [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a dual clutch transmission, and more particularly, to a dual clutch transmission capable of simplifying a structure and capable of simply shifting.

Unlike a conventional single-plate clutch transmission system, the dual-clutch transmission has two clutches, one of which is designed to form a separate transmission system that allows the one-way clutch and the other of the clutches to be interlocked As a transmission system, it is widely used because it is easy to operate, has less power loss, and has a faster shift time.

For example, assuming that the dual clutch transmission shifts from the first stage to the sixth stage, if the first clutch is traveling in one stage, the second clutch has already been shifted to the second stage. When the shifting is started, the power of the first clutch is cut off and the second clutch is engaged. For example, when the vehicle enters the second-stage traveling, the first clutch disengages the first-gear and shifts to the third-gear so as to wait for the clutch to be engaged for the next shift. Due to these characteristics, the dual clutch transmission has a faster shift time and a shorter shift time than the manual transmission.

In general, the shifting of the dual clutch transmission can be achieved by moving the shift fork holding the synchronizer disposed between the gears of the respective stages and selecting the gear ratio of the desired gear stage. For example, the conventional shift fork is mounted on a fork rod so as to be linearly movable along an axial direction, and is configured to be linearly moved by a barrel cam rotated by a driving motor.

In this connection, a "shift device of a dual clutch transmission" is disclosed in Japanese Patent Registration No. 10-1034890. The shift device includes a first input shaft and a second input shaft which are connected to the first clutch and the second clutch, respectively. The two input shafts are suitably provided with drive gears for the first to seventh gears, A counter shaft and a second counter shaft are provided with driven gears engaging the drive gears.

Approximately four synchronizers are provided between driven gears and one barrel cam is provided adjacent to the fork rod to operate four shift forks for four synchronizers. The shift fork includes a follow pin, and the shift fork can be positioned at the right, left, or intermediate position as the follow pin moves along the cam groove of the barrel cam.

The shifting device shifts from the first stage to the seventh stage. The shift forks from the fifth stage to the seventh stage in the section shifted from the first stage to the third stage maintain the neutral (N) The shift fork from the first stage to the third stage also maintains the neutral (N). That is, when one barrel cam is used, the follow pin of the shift fork is stopped at the intermediate position of the cam groove, and generally half of the entire circumference is resting in the resting period.

The long idle period means that the cam structure becomes complicated and it means that the diameter and weight of the barrel cam naturally increase because the cam groove of the barrel cam can not form a steep gradient of the speed change section. As a result, the increase in the diameter of the barrel cam increases the space of the barrel cam in the transmission, which may hinder the compact design. The increase in weight means that the inertia moment of the barrel cam increases, The cost of the system increases.

Accordingly, in recent years, various researches have been made on a dual clutch transmission that can simplify the structure and facilitate shift control, but it is still insufficient and development thereof is urgently required.

The present invention provides a dual clutch transmission capable of simplifying the structure and facilitating shift control.

In particular, the present invention provides a dual clutch transmission device capable of controlling the shift using a single drive motor.

Further, the present invention provides a dual clutch transmission capable of reducing cost and improving vehicle mountability.

According to a preferred embodiment of the present invention, a dual clutch transmission including a first counter shaft and a second counter shaft for moving a synchronizer to realize a shift, A first shift fork unit for moving a synchronizer adjacent to the first counter shaft to perform a shift operation, a second shift fork unit for performing a shift operation by moving a synchronizer adjacent to the second counter shaft, A drive motor for providing a drive force for driving the first shift fork unit and the second shift fork unit and a switch unit for selectively transmitting the drive force of the drive motor to either the first shift fork unit or the second shift fork unit.

The switch unit may be provided with various structures capable of selectively transmitting the driving force of the driving motor to either the first shift fork unit or the second shift fork unit.

For example, the switch unit may be configured to transmit the driving force of the driving motor to either the first shift fork unit or the second shift fork unit according to the rotational direction of the driving motor. More specifically, the switch portion is provided with a switching wheel integrally coupled to a drive shaft of the drive motor and rotated together with the drive shaft, a switch wheel provided on one surface of the switch wheel so as to idle with respect to the switch wheel, And a second switching gear provided on the other surface of the switching wheel so as to be idly rotatable with respect to the switching wheel and rotating together with the switching wheel only in the other one direction rotation of the switching wheel, , The first shift fork unit can perform the shift operation corresponding to the rotation of the first switching gear and the second shift fork unit can perform the shift operation corresponding to the rotation of the second switching gear.

The first switch gear and the second switch gear are configured to selectively rotate and rotate by the switching wheel in accordance with the rotation direction of the switching wheel so that the selective interlocking structure between the switching wheel and the first switch gear and the second switch gear is required And can be variously changed depending on conditions and design specifications. For example, a first switching groove having a depth gradient along the circumferential direction may be formed on one surface of the switching wheel, and the first switching gear may be elastically provided on one surface of the switching wheel so as to be rotatable in a clockwise direction A first switching rod may be provided which is constrained to the first switching groove only in correspondence to the rotation in either one of the rotation and the counterclockwise rotation. A second switching groove having a depth gradient along the circumferential direction may be formed on the other surface of the switching wheel. The second switching gear may be elastically provided on the other surface of the switching wheel, A second switching rod may be provided which is constrained to the second switching groove only in correspondence with the rotation in the other direction during the directional rotation and the counterclockwise rotation.

In the present invention, the first switching groove and the second switching groove have a depth gradient along the circumferential direction. The first switching groove and the second switching groove have a first switching groove and a second switching groove formed along the circumferential direction of the first switching gear and the second switching gear, It can be understood that the switching groove gradually has a deep depth (or a shallow depth) as it goes from one end to the other end. The first switching groove and the second switching groove may have an entry portion having a relatively shallow depth at one end and a step portion having a relatively deep depth at the other end, The first switching groove and the second switching groove. For example, an arc-shaped first switching groove may be formed on one surface of the switching wheel with respect to the first switch gear so as to have a gradually deeper depth along the counterclockwise direction, And a circular arc-shaped second switching groove may be formed on the one surface so as to have a gradually deeper depth along the counterclockwise direction.

The first shift fork unit and the second shift fork unit may be provided in various structures capable of shifting operations corresponding to the rotation of the first switch gear and the second switch gear. For reference, in the present invention, the shift operation is performed by the first shift fork unit and the second shift fork unit in correspondence with the rotation of the first switch gear and the second switch gear. The first switch gear and the second switch gear It can be understood that the first shift fork unit and the second shift fork unit are operated and the corresponding synchronizer is shifted to perform shifting.

In one example, the first shift fork unit includes a first gear engaged with the first switching gear, a first fork rod rotating with the first gear, and a second fork rod connected to the synchronizer, And a first fork that linearly moves along the first fork rod in response to the first fork rod. The first shift fork unit may include a cam member or a link member that can be interlocked by the rotation of the first switching gear and is interlocked by the rotation of the first switching gear, Or any other structure that can be moved.

The structure in which the first fork is interlocked by the rotation of the first fork rod can be variously changed in accordance with required conditions and design specifications. For example, a first cam groove may be formed on an outer circumferential surface of the first fork rod, a first cam protrusion may be formed on the first fork to be accommodated in the first cam groove, As the cam protrusion moves along the first cam groove, the first fork can move linearly with respect to the first fork rod. In some cases, the first fork may be linearly moved as the cam member rotates by the rotation of the first fork rod by using a separate cam member, and the first fork may be linearly moved by the rotation of the first fork rod 1 fork can be configured to be interlocked.

The second shift fork unit may further comprise a second gear engaged with the second switching gear, a second fork rod rotating together with the second gear, and a second fork rod connected to the synchronizer and corresponding to the rotation of the second fork rod, And a second fork that moves linearly along the first fork. The second shift fork unit may include a cam member or a link member that can be interlocked by the rotation of the second switching gear, and may be interlocked by the rotation of the second switching gear, Or any other structure that can be moved. Alternatively, the first shift fork unit and the second shift fork unit may have different structures.

The structure in which the second fork is interlocked by the rotation of the second fork rod can be variously changed according to the required conditions and design specifications. For example, a second cam groove may be formed on the outer circumferential surface of the second fork rod, a second cam protrusion may be formed on the second fork to be accommodated in the second cam groove, As the cam protrusion moves along the second cam groove, the second fork can move linearly with respect to the second fork rod.

On the other hand, a separate cam member such as a barrel cam may be configured to rotate in correspondence with the rotation of the first switch gear and the second switch gear, or the fork may be moved by the rotation of the cam member so as to implement a shift Do.

According to another preferred embodiment of the present invention, the first shift fork unit includes a first gear engaged with the first switching gear, a first cam groove formed along the outer circumferential surface, and integrally coupled to the rotation shaft of the first gear A first cam member which is connected to the synchronizer and moves along the first cam groove in correspondence to the rotation of the first cam member and which moves linearly along the axial direction of the first cam member, And a fork. The second shift fork unit includes a second gear engaged with the second switching gear, a second gear formed along the outer circumferential surface thereof, a second cam groove formed integrally with the rotation shaft of the second gear, And a second fork connected to the second cam member and moving along the second cam groove corresponding to the rotation of the second cam member and linearly moving along the axial direction of the second cam member.

According to another preferred embodiment of the present invention, the switch portion can be configured to transmit the driving force of the drive motor to either the first shift fork unit or the second shift fork unit according to the rotation angle of the drive motor.

For example, the first shift fork unit may include a first barrel cam member for actuating a first fork mounted on a first fork rod adjacent the first counter shaft, and the second shift fork unit may comprise a second counter- And a second barrel cam member for actuating a second fork mounted on a second fork rod adjacent to the second barrel cam member, wherein the switch section comprises a first select gear mounted on a shaft of the first barrel cam member, And a switching gear for selectively transmitting power to any one of the first and second selection gears. The first and second selection gears may be exclusively provided with the switching gear Can be connected.

In addition, a stop value including a geneva gear surface may be provided between the gear teeth of the first and second selectable gears, and rotation of the first or second select gear during the engagement of the geneva gear surface with the stop gear at the non- It is also possible to arrange to be constrained.

According to the dual clutch transmission according to the present invention, the structure can be simplified and the shift control can be easily performed.

Particularly, according to the present invention, it is not necessary to individually provide a drive motor for operating the first shift fork unit and the second shift fork unit, and the drive force by the single drive motor is selectively transmitted to the first shift fork unit And the second shift fork unit. Therefore, the structure can be simplified, and only one motor can be controlled, which is advantageous in that the shift control is easier.

Further, according to the present invention, since only one drive motor is used, it is possible to contribute to downsizing of the apparatus, cost reduction, and vehicle mountability.

Further, according to the present invention, there is an advantage that the number of shift stages can be increased by adjusting the resolution of the switch section.

1 is a view for explaining a configuration of a dual clutch transmission according to the present invention.
2 to 4 are views showing a structure of a dual clutch transmission according to the present invention.
5 and 6 are views for explaining the operating structure of the dual clutch transmission according to the present invention.
7 is a view showing a structure of a dual clutch transmission according to another embodiment of the present invention.
8 and 9 are views for explaining a cam groove of a fork rod as a dual clutch transmission according to another embodiment of the present invention.
10 to 12 are views showing a structure of a dual clutch transmission according to another embodiment of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. However, the present invention is not limited to the embodiments. For reference, the same numbers in this description refer to substantially the same elements and can be described with reference to the contents described in the other drawings under the above-mentioned rules, and the contents which are judged to be obvious to the person skilled in the art or repeated can be omitted.

FIG. 1 is a view for explaining a configuration of a dual clutch transmission according to the present invention, FIGS. 2 to 4 are views showing a structure of a dual clutch transmission according to the present invention, Fig. 3 is a view for explaining an operating structure of the dual clutch transmission device according to the first embodiment;

1 to 6, a dual clutch transmission according to the present invention includes a transmission portion and a shift portion.

The transmission unit includes a dual clutch 13 including a first clutch 11 and a second clutch 12, a first input shaft 21 and a second input shaft 22 of the first and second clutches 11 and 12, And a plurality of driven gears G1 to G8 mounted on the first counter shaft 23 and the second counter shaft 24, respectively.

The rotational force generated in the engine can be selectively transmitted to the first clutch 11 or the second clutch 12 and the rotational force transmitted to the first clutch 11 or the second clutch 12 is transmitted to the first input shaft 21 ) Or the second input shaft 22, as shown in Fig.

As the dual clutch including the first clutch 11 and the second clutch 12, a conventional dual clutch may be used, and the present invention is not limited or limited by the type and characteristics of the dual clutch. For example, the first clutch 11 and the second clutch 12 may be configured to transmit the rotational force of the engine to the first input shaft 21 or the second input shaft 22 through normal hydraulic control.

The first input shaft 21 is connected to the first clutch 11 and can receive the rotational force generated by the engine. The second input shaft 22 is disposed on the same axis as the first input shaft 21 and connected to the second clutch 12 to receive the rotational force generated by the engine. For this, the second input shaft 22 may be hollow and the first input shaft 21 may be disposed inside the second input shaft 22.

The first counter shaft 23 and the second counter shaft 24 are disposed in parallel with the first input shaft 21 and the second input shaft 22 and are connected to the first input shaft 21 and the second input shaft 22 And the rotational force generated from the engine is transmitted.

The plurality of driving gears D1 to D8 are connected to the first input shaft 21 and the second input shaft 22 and have different gear ratios, that is, speed ratios. More specifically, the Hall device driving gears D1, D3, D5 and D7 of the plurality of driving gears D1 to D8 may be connected to the first input shaft 21 and the even numbered driving gears D2, D4, D6 and D8 May be connected to the second input shaft 22.

The plurality of driven gears G1, G2, G3, G4, G5, G6, G7 and G8 are respectively provided in the first counter shaft 23 and the second counter shaft 24 and have different gear ratios . The first driven gear G1, the fifth driven gear G5, the second driven gear G2, and the second driven gear G3 among the plurality of driven gears G1, G2, G3, G4, G5, G6, G7, The sixth driven gear G6 can be installed on the second counter shaft 24 without rotation intervention and the third driven gear G3, the seventh driven gear G7, the fourth driven gear G4, The gear G8 can be installed on the first counter shaft 23 without rotating interference.

The first to fourth synchronizers 31, 32, 33 and 34 are provided between the driven gears G1, G2, G3, G4, G5, G6, G7 and G8. That is, the first to fourth synchronizers 31, 32, 33, and 34 are disposed so as to be positioned between the corresponding driven gears G1, G2, G3, G4, G5, G6, G7, And is installed in the counter shaft 23 and the second counter shaft 24, respectively.

For example, the first synchronizer 31 is provided so as to be spline-coupled to the second counter shaft 24 so as to be positioned between the sixth driven gear G6 and the second driven gear G2, Can be shifted by the second shift fork unit 320 to be described later to be engaged with the gear G6 or the second driven gear G2. The second synchronizer 32 is disposed on one side of the first synchronizer 31 and spline coupled to the second counter shaft 24 so as to be positioned between the fifth driven gear G5 and the first driven gear G1. And can be shifted by the second shift fork unit 320 so as to be fastened to the fifth driven gear G5 or the first driven gear G1. The third synchronizer 33 is arranged to face the first synchronizer 31 and is disposed on the first counter shaft 23 so as to be positioned between the eighth driven gear G8 and the fourth driven gear G4 And can be shifted by the first shift fork unit 310 to be described later so as to be coupled to the eighth driven gear G8 or the fourth driven gear G4. The fourth synchronizer 34 is disposed on one side of the third synchronizer 33 and spline coupled to the first counter shaft 23 so as to be positioned between the seventh driven gear G7 and the third driven gear G3. And can be shifted by the first shift fork unit 310 to be engaged with the seventh driven gear G7 or the third driven gear G3.

As the first to fourth synchronizers 31, 32, 33, and 34, a conventional synchronizer may be used, and the present invention is not limited or limited by the types and characteristics of the synchronizer. For example, the sleeve or the like of the synchronizer is coupled to the counter shaft by spline coupling and is movable in the axial direction. When the synchronizer approaches and engages one of the driven gears, power can be transmitted through the engaged driven gear and drive gear, and the counter shaft can transmit power through the other output shaft. The structure of a specific synchronizer can refer to a conventional structure.

The first to fourth synchronizers 31, 32, 33 and 34 are provided with first forks 316a and 316b and second forks 326a and 326b of the first and second shift fork units 310 and 320, respectively. The first to fourth synchronizers 31, 32, 33, and 34 may be provided with first and second forks 316a and 316b and second forks 326a and 326b (not shown) The rotation of the driven gears G1, G2, G3, G4, G5, G6, G7 and G8 is synchronized with the first counter shaft 23 and the second counter shaft 24, Let's do it.

The shift portion is provided for shifting the transmission gear portion and includes a first shift fork unit 310, a second shift fork unit 320, a drive motor 100, and a switch portion 200.

The first shift fork unit 310 is configured to perform a shift operation by moving the synchronizers 33 and 34 adjacent to the first counter shaft 23, The structure of the first shift fork unit 310 and the second shift fork unit 320 is configured so as to be capable of performing a shift operation by moving the synchronizers 31 and 32 adjacent to the two counter shafts 24, And can be variously changed according to the design conditions and the design specifications.

The drive motor 100 provides a driving force for driving the first shift fork unit 310 and the second shift fork unit 320. [ As the driving motor 100, a conventional motor can be used, and the present invention is not limited or limited by the type and characteristics of the motor. In some cases, other driving means such as a solenoid may be used instead of a motor.

The switch unit 200 is configured to selectively transmit the driving force of the driving motor 100 to either the first shift fork unit 310 or the second shift fork unit 320. The first shift fork unit 310, And the second shift fork unit 320 can be selectively operated by receiving the driving force of the driving motor 100 by the switch unit 200.

The switch unit 200 may be provided with various structures capable of selectively transmitting the driving force of the driving motor 100 to either the first shift fork unit 310 or the second shift fork unit 320.

For example, the switch unit 200 may transmit the driving force of the driving motor 100 to either the first shift fork unit 310 or the second shift fork unit 320 according to the rotational direction of the driving motor 100 Lt; / RTI >

2 to 4, the switch unit 200 includes a switching wheel 230 integrally coupled to a driving shaft of the driving motor 100 and rotated together with a driving shaft, A first switching gear 210 provided on one surface of the switching wheel 230 and rotating together with the switching wheel 230 only in one direction rotation of the switching wheel 230, And a second switching gear 220 which is provided on the other surface of the switching wheel 230 and rotates together with the switching wheel 230 in correspondence with another one direction rotation of the switching wheel 230, The first shift fork unit 310 can perform a shift operation corresponding to the rotation of the first switching gear 210 and the second shift fork unit 320 can perform the shift operation corresponding to the rotation of the second switching gear 220 So that the shift operation can be performed.

The switching wheel 230 is provided between the first switching gear 210 and the second switching gear 220 and is integrally coupled to the driving shaft of the driving motor 100 and is driven by a driving force of the driving motor 100 It can rotate clockwise or counterclockwise.

The first switching gear 210 is provided to rotate corresponding to rotation of the switching wheel 230 in any one of clockwise rotation and counterclockwise rotation. For example, the first switching gear 210 may be rotated by the switching wheel 230 in response to only the clockwise rotation of the switching wheel 230, and the switching wheel 230 may be rotated counterclockwise The rotational force of the switching wheel 230 is not transmitted to the first switching gear 210 but only the switching wheel 230 is rotated.

The second switching gear 220 is provided so as to rotate corresponding to rotation of the other one of the clockwise rotation and the counterclockwise rotation of the switching wheel 230. For example, the second switching gear 220 may be rotated by the switching wheel 230 in response to the counterclockwise rotation of the switching wheel 230, and the switching wheel 230 may rotate clockwise The rotational force of the switching wheel 230 is not transmitted to the second switching gear 220 but only the switching wheel 230 is rotated.

As the first switching gear 210 and the second switching gear 220, a spur gear having teeth parallel to the axis along the outer circumferential surface may be used, but in some cases, the first switching gear and the second switching gear Other gears may be used.

As described above, the first switching gear 210 and the second switching gear 220 are selectively coupled to and rotated by the switching wheel 230 according to the rotation direction of the switching wheel 230, The shift fork unit 310 and the second shift fork unit 320 are operated by rotation of the first switching gear 210 and the second switching gear 220 and are configured to perform a shift operation.

The selectively interlocking structure between the switching wheel 230 and the first and second switching gears 210 and 220 can be variously changed according to required conditions and design specifications.

For example, the first switching groove 232 having a depth gradient along the circumferential direction may be formed on one surface of the switching wheel 230, and the first switching gear 210 may be mounted on one surface of the switching wheel 230 A first switching rod 212 is provided that is sexually accessible so that it is constrained to the first switching groove 232 only in response to rotation of the switching wheel 230 in either the clockwise or counterclockwise direction .

A second switching groove 234 having a depth gradient along the circumferential direction may be formed on the other surface of the switching wheel 230 and a second switching groove 234 may be formed on the other surface of the switching wheel 230 A second switching rod 222 is provided that is elastically accessible so that it is constrained to the second switching groove 234 only in the counterclockwise and counterclockwise rotation of the switching wheel 230, Can be provided.

The first switching rod 212 and the second switching rod 222 are supported by conventional spring members 214 and 224 and resiliently contact the corresponding first switching gear 210 and the second switching gear 220, . In some cases, other elastic members may be used in place of the spring members, and the present invention is not limited or limited by the elastic supporting structure of the first switching rod and the second switching rod.

The first switching groove 232 and the second switching groove 234 have a depth gradient along the circumferential direction of the first switching gear 210 and the second switching gear 220, The first switching groove 232 and the second switching groove 234 formed along the direction of the first switching groove 234 may have a gradually increasing depth (or a shallow depth) from one end to the other end. The first switching groove 232 and the second switching groove 234 may have a relatively shallow depth portion 232a or 234a at one end and a relatively deep depth portion 232b or 232b at the other end, The first switching rod 212 and the second switching rod 222 may be formed in the first switching groove 232 and the second switching groove 234 in the stepped portions 232b and 234b, . For example, an arc-shaped first switching groove 232 may be formed on one surface of the switching wheel 230 with respect to the first switching gear 210 so as to have a gradually deeper depth along the counterclockwise direction, An arc-shaped second switching groove 234 may be formed on the other surface of the switching wheel 230 with respect to the switching gear 220 so as to have a gradually deeper depth along the counterclockwise direction.

According to this structure, when the switching wheel 230 rotates in the clockwise direction, the first switching rod 212 can be confined to the step portion 232b of the first switching groove 232, The first switching gear 210 is also linked to the switching wheel 230 in the clockwise direction by the constraint between the rod 212 and the first switching groove 232 so that the first switching gear 210 rotates clockwise. In addition, when the switching wheel 230 rotates clockwise, since the second switching rod 222 moves in the direction of the entering portion 234a from the step portion 234b of the second switching groove 234, The torque of the wheel is not transmitted to the second switching gear 220.

On the contrary, when the switching wheel 230 rotates counterclockwise, the second switching rod 222 can be constrained to the step 234b of the second switching groove 234, and the second switching rod 222 and the second switching groove 234, the second switching gear 220 is also interlocked with the switching wheel 230 in the counterclockwise direction and can be rotated counterclockwise. In addition, when the switching wheel 230 rotates counterclockwise, since the first switching rod 212 moves in the direction of the entrance portion 232a from the step portion 232b of the first switching groove 232, The rotational force of the switching wheel is not transmitted to the first switching gear 210.

The first shift fork unit 310 and the second shift fork unit 320 are provided with various structures capable of shifting operation corresponding to the rotation of the first switching gear 210 and the second switching gear 220 . For reference, in the present invention, the first shift fork unit and the second shift fork unit perform the shift operation in response to the rotation of the first switching gear and the second switching gear, the first switching gear and the second switching gear It can be understood that the first shift fork unit and the second shift fork unit are operated and the corresponding synchronizer is shifted to perform shifting.

For example, the first shift fork unit 310 includes a first gear 210 engaged with the first switching gear 210, a first fork rod 314 rotated together with the first gear 210 And a first fork (not shown) connected to the aforementioned synchronizer (see 33 and 34 in FIG. 1) and linearly moving along the first fork rod 314 in correspondence with the rotation of the first fork rod 314 316a, and 316b. The first shift fork unit may include a cam member or a link member that can be interlocked by the rotation of the first switching gear and is interlocked by the rotation of the first switching gear, Or any other structure that can be moved.

The first gear 210 rotates in conjunction with the rotation of the first switching gear 210. When the first gear 210 rotates and the first gear 210 rotates, The fork rod 314 can rotate together and the rotation of the first fork rod 314 allows the first fork 316a and 316b to move linearly along the first fork rod 314. [ A first cam groove 314a is formed on the outer circumferential surface of the first fork rod 314 and a first cam protrusion 317 accommodated in the first cam groove 314a is formed in the first forks 316a and 316b As the first cam protrusion 317 moves along the first cam groove 314a corresponding to the rotation of the first fork rod 314, the first fork 316a, 316b is moved to the first fork rod 314 (Refer to FIG. 4). In some cases, as the cam member rotates by the rotation of the first fork rod by using a separate cam member, the first fork is moved in a straight line And the first fork can be configured to be interlocked by rotation of the first fork rod with other structures.

The first cam protrusion 317 can be circulated and moved along the first cam groove 314a as the first fork rod 314 rotates and the angle and structure of the first cam groove 314a can be changed according to the required conditions and design It can be changed appropriately according to specifications. The gear ratio between the first switching gear 210 and the first gear 210 may be appropriately changed according to required conditions and design specifications. For example, when the first switching gear 210 rotates by 1/2, the first gear 210 may rotate by one rotation.

The second shift fork unit 320 includes a second gear 220 engaged with the second switching gear 220, a second fork rod 324 rotated together with the second gear 220, And second forks 326a and 326b connected to the first fork rod 324 (see FIGS. 1 and 31) and linearly moving along the second fork rod 324 in correspondence with the rotation of the second fork rod 324 . The second shift fork unit may include a cam member or a link member that can be interlocked by the rotation of the second switching gear, and may be interlocked by the rotation of the second switching gear, Or any other structure that can be moved. For reference, in the embodiment of the present invention, the first shift fork unit and the second shift fork unit have the same structure. However, in some cases, the first shift fork unit and the second shift fork unit It may be of other structure.

The second gear 220 may rotate and rotate as the second switching gear 220 rotates and may rotate in a second direction in which the second gear 220 rotates, The second forks 326a and 326b can be moved linearly along the second fork rod 324 by the rotation of the second fork rod 324. [ A second cam groove 324a is formed in the outer circumferential surface of the second fork rod 324 and a second cam protrusion 327 accommodated in the second cam groove 324a is formed in the second fork 326a and 326b And as the second cam protrusion 327 moves along the second cam groove 324a in correspondence with the rotation of the second fork rod 324, the second fork 326a and 326b move toward the second fork rod 324 As shown in FIG. In some cases, the second fork may be linearly moved as the cam member rotates by the rotation of the second fork rod using a separate cam member, and the second fork may be linearly moved by rotation of the second fork rod Two forks can be configured to work together.

The second cam protrusion 327 can be circulated and moved along the second cam groove 324a as the second fork rod 324 rotates and the angle and structure of the second cam groove 324a can be changed according to the required conditions and design It can be changed appropriately according to specifications. The gear ratio between the second switching gear 220 and the second gear 220 can be appropriately changed according to required conditions and design specifications. For example, when the second switching gear 220 rotates by 1/2, the second gear 220 may rotate by one rotation.

Hereinafter, the operating structure of the dual clutch transmission according to the present invention will be described with reference to FIGS. 5 and 6. FIG.

5, when the switching wheel 230 rotates in the clockwise direction, the first switching gear 210 is coupled to the switching wheel 230 as the first switching rod 212 is constrained to the first switching groove 232, And rotates in the clockwise direction. When the first switching gear 210 rotates, the first gear 210 coupled to the first switching gear 210 rotates and the first fork rod 314 rotates. At the same time, the first fork rod 314 The first forks 316a and 316b move linearly with respect to the first fork rod 314 as the first cam protrusion 317 moves along the first cam groove 314a corresponding to the rotation of the first fork 314, (See Figs. 33 and 34 in Fig. 1). When the switching wheel 230 rotates in the clockwise direction, the rotational force of the switching wheel 230 is not transmitted to the second switching gear 220, so that the second switching gear 220 rotates to the switching wheel 230 .

Referring to FIG. 6, when the switching wheel 230 rotates in the counterclockwise direction, the second switching gear 220 is coupled to the switching wheels 230 (230) as the second switching rod 222 is constrained to the second switching groove 234, ) And is rotated counterclockwise. When the second switching gear 220 rotates, the second gear 220 coupled to the second switching gear 220 rotates and the second fork rod 324 rotates. At the same time, the second fork rod 324 The second forks 326a and 326b move linearly with respect to the second fork rod 324 as the second cam protrusion 327 moves along the second cam groove 324a corresponding to the rotation of the second fork rod 324, (See 31 and 32 in Fig. 1) to realize the shifting. When the switching wheel 230 rotates counterclockwise, the rotational force of the switching wheel 230 is not transmitted to the first switching gear 210, so that the first switching gear 210 rotates the switching wheel 230, Lt; / RTI >

7 is a view illustrating a dual clutch transmission according to another embodiment of the present invention. In addition, the same or equivalent portions as those in the above-described configuration are denoted by the same or equivalent reference numerals, and a detailed description thereof will be omitted.

Referring to FIG. 7, a dual clutch transmission according to another embodiment of the present invention includes a driving motor 100, a switching wheel 230 integrally coupled to the driving shaft of the driving motor 100 and rotated together with the driving shaft, A first switching gear 210 provided on one surface of the switching wheel 230 so as to idle with respect to the switching wheel 230 and rotating together with the switching wheel 230 only in one direction of the switching wheel 230, And a second switching gear 220 provided on the other surface of the switching wheel 230 so as to idle with respect to the switching wheel 230 and rotated together with the switching wheel 230 in correspondence with the other one direction rotation of the switching wheel 230 A first shift fork unit 310 'for shifting the synchronizer (see 31-34 in FIG. 1) corresponding to the rotation of the first switching gear 210 to perform a shift operation, 2 synchronizer in response to the rotation of the switching gear 220, The first shift fork unit 310 'includes a first gear 312' engaged with the first switching gear 210, and a second shift fork unit 320 ' A first cam member 318 'which is integrally coupled to the rotation shaft 314' of the first gear 312 'and rotates together with the first gear 312', a first cam groove 318a 'formed along the outer circumferential surface, Which moves along the first cam groove 318a 'in accordance with the rotation of the first cam member 318' and is linearly moved along the axial direction of the first cam member 318 ' The second shift fork unit 320 may include a second gear 322 'engaging with the second switching gear 220. The second shift fork unit 320' may include a fork 316a 'and 316b' A second cam member 328a 'which is formed integrally with the rotation shaft 324' of the second gear 322 'and rotates together with the second gear 322', a second cam groove 328a 'is formed along the outer circumferential surface, ) And a second cam member (328 ') connected to the synchronizer And second forks 326a 'and 326b which move along the second cam groove 328a' in accordance with the axial movement of the second cam member 328 'and linearly move along the axial direction of the second cam member 328'.

For reference, the profiles of the first and second cam grooves 318a 'and 328a' may be appropriately changed according to required conditions and design specifications, and the profiles of the first and second cam grooves 318a ' But are not limited to. 8, the first cam groove 318a 'and the second cam groove 328a' are formed such that both end portions of the first cam member 318 'and the second cam member 328' And the first forks 316a 'and 316b' and the second forks 326a 'and 326b may be formed as a first cam member 318' and a second cam member 328 ' It can circulate and move along the cam groove 318a 'and the second cam groove 328a'.

In the above-described embodiment, the first cam groove and the second cam groove are formed so as to be continuous with each other. However, in some cases, both ends of the first and second cam grooves may be separated.

9, both ends of the first and second cam grooves 318a " (or second cam grooves) may be separated from each other to provide a broken path. In this way, both ends of the first and second cam grooves 318a " In the separated mode, the synchronizer can be moved to a desired position while the first cam member and the second cam member are rotated forward or reverse. The first cam groove (or the second cam groove) The angular range formed on the outer surface of the member can be extended to 360 degrees or more and the length of the first cam groove can be made longer within a range in which the first cam grooves do not overlap with each other.

In the embodiment of the present invention, a plurality of cam grooves are formed in the first cam member and the second cam member. However, in some cases, the first cam member and the second cam member may have a single cam groove, May be provided.

With this structure, when the switching wheel 230 rotates in the clockwise direction, the first switching gear (see 212 in FIG. 3) is confined to the first switching groove (see 232 in FIG. 3) 210 are interlocked by the switching wheel 230 and rotate clockwise. When the first switching gear 210 rotates, the first gear 312 'engaged with the first switching gear 210 rotates and the first cam member 318' can rotate at the same time, The first forks 316a 'and 316b' move along the first cam groove 318a 'and move linearly along the axial direction of the first cam member 318' corresponding to the rotation of the first cam member 318 ' The shift can be implemented by moving the niger. When the switching wheel 230 rotates in the clockwise direction, the rotational force of the switching wheel 230 is not transmitted to the second switching gear 220, so that the second switching gear 220 rotates to the switching wheel 230 .

Conversely, when the switching wheel 230 rotates counterclockwise, the second switching gear 220 (refer to 222 in FIG. 3) is restrained by the second switching groove (see 234 in FIG. 3) Is rotated by the switching wheel (230) and rotated counterclockwise. When the second switching gear 220 rotates, the second gear 322 'engaged with the second switching gear 220 rotates and the second cam member 328' can rotate at the same time, The second forks 326a 'and 326b' move along the second cam groove 328a 'and move linearly along the axial direction of the second cam member 328' corresponding to the rotation of the second cam member 328 ' The shift can be implemented by moving the niger. When the switching wheel 230 rotates counterclockwise, the rotational force of the switching wheel 230 is not transmitted to the first switching gear 210, so that the first switching gear 210 rotates the switching wheel 230, Lt; / RTI >

10 to 12 are views showing the structure of a dual clutch transmission according to another embodiment of the present invention. In addition, the same or equivalent portions as those in the above-described configuration are denoted by the same or equivalent reference numerals, and a detailed description thereof will be omitted.

According to another embodiment of the present invention, the switch unit may be configured to transmit the driving force of the driving motor to either the first shift fork unit or the second shift fork unit according to the rotation angle of the driving motor.

For example, the first shift fork unit 1310 may include a first fork 326a, 326b mounted on a first fork rod 324 adjacent a first counter shaft (see 24 in FIG. 1) Barrel cam member 1250 and the second shift fork unit 1320 may include a second fork 316a mounted on a second fork rod 314 adjacent to a second counter shaft And a second barrel cam member 1240 for actuating the first barrel cam member 1230 and the second barrel cam member 1230. The switch unit 1200 may include a first select gear 1210 mounted on the shaft of the first barrel cam member 1250, A second selection gear 1220 mounted on the shaft of the barrel cam member 1240 and a switching gear 1230 selectively transmitting power to either the first or second selection gear 1210 or 1220 Lt; / RTI >

10 is a view for explaining a cam driving unit of the transmission according to another embodiment of the present invention, and FIG. 11 is a side view for explaining the switch unit of FIG.

10 and 11, the transmission includes one drive motor 100 and a switch portion 1200, and selectively connects the first barrel cam member 1250 or the second barrel cam member 1250 using the switch portion 1200. [ The barrel cam member 1240 can be rotated.

For reference, in the present embodiment, it is described that the first barrel cam member 1250 or the second barrel cam member 1240 is selectively operated according to the rotation angle by using a toothless gear having no gear teeth partially, In addition, a switch portion such as a one-way clutch that selectively operates some of the two or more barrel cam members along the rotational direction can be also provided.

Referring again to FIGS. 10 and 11, the cam driver includes one drive motor 100 for the first and second barrel cam members 1250 and 1240 and one of the first and second barrel cam members 1250 and 1240 And a switch unit 1200 for transmitting the power of the one-way drive motor 100. The switch unit 1200 includes a first select gear 1210 mounted on an axis of the first barrel cam member 1250, A second select gear 1220 mounted on the shaft of the cam member 1240 and a switching gear 1230 disposed between the first and second select gears 1210 and 1220. [

The switching gear 1230 is formed with gear teeth at an angle of about 180 degrees and the gear teeth are formed at an opposite 180 degree angle. Thus, it can engage with the first select gear 1210 at 180 degree rotation and with the second select gear 1220 at the opposite 180 degree rotation.

The switching gear 1230 includes a gear surface and a toothless surface. The switching gear 1230 can be meshed with the first or second select gears 1210 and 1230 by a gear face and can be driven and disengaged from the first or second select gears 1210 and 1230 by a toothless surface Can be achieved. Here, the drivingly separated state includes a state in which the power can not be physically separated and can not transmit power even though it is physically connected. The first and second selection gears 1210 and 1220 can be exclusively connected to the switching gear 1230 by a combination of a gear surface and a toothless surface. In some cases, they may form partly moving sections.

12 is a side view for explaining a switch portion of the transmission according to another embodiment of the present invention, which is similar to the switch portion of FIG.

12, the switch unit includes a first gear 1210 ', a second select gear 1220', and a switching gear 1230 'disposed between the first and second select gears 1210' and 1220 ' ). The switching gear 1230 'provides a gear face at which gear teeth are formed at an angle of about 180 degrees and a zero tooth face at which gear teeth are removed at an opposite 180 degree angle.

The first select gear 1210 'and the second select gear 1220' may further include stop teeth 1212 'and 1222' including at least one Geneva gear surface between the gear teeth. If the generator or gear surfaces of the stop teeth 1212 'and 1222' are maintained in a state of being in contact with the toothless surface, even if the first or second select gear 1210 'or 1220' is powered off from the toothless surface, The rotation can be constrained to maintain the state.

Although the preferred embodiments of the present invention have been disclosed for illustrative purposes, those skilled in the art will appreciate that various modifications, additions and substitutions are possible, without departing from the scope and spirit of the invention as disclosed in the accompanying claims. It will be understood that the present invention can be changed.

100: drive motor 200: switch part
310: first shift fork unit 320: second shift fork unit

Claims (11)

A dual clutch transmission device for shifting a synchronizer in a dual clutch including a first counter shaft and a second counter shaft,
A first shift fork unit for shifting the synchronizer adjacent to the first counter shaft to perform a shift operation;
A second shift fork unit for shifting the synchronizer adjacent to the second counter shaft to perform a shift operation;
A drive motor for providing a driving force for driving the first shift fork unit and the second shift fork unit; And
A switch unit selectively transmitting the driving force of the driving motor to either the first shift fork unit or the second shift fork unit;
And a second clutch. The method according to claim 1,
Wherein the switching unit transmits the driving force of the driving motor to any one of the first shift fork unit and the second shift fork unit according to the rotational direction of the drive motor. 3. The method of claim 2,
Wherein,
A switching wheel integrally coupled to a driving shaft of the driving motor and rotating together with the driving shaft;
A first switching gear provided on one surface of the switching wheel so as to be able to idle with respect to the switching wheel and rotated together with the switching wheel only in one direction rotation of the switching wheel;
And a second switching gear provided on the other surface of the switching wheel so as to be capable of idling with respect to the switching wheel and rotating together with the switching wheel only in the other one direction rotation of the switching wheel,
Wherein the first shift fork unit performs a shift operation corresponding to the rotation of the first switching gear and the second shift fork unit performs a shift operation corresponding to the rotation of the second switching gear. Clutch transmission. The method of claim 3,
Wherein a first switching groove and a second switching groove having a depth gradient along a circumferential direction are formed on one surface and the other surface of the switching wheel,
A first switching rod provided on the first switching gear so as to be elastically accessible to one surface of the switching wheel and confined to the first switching groove only in one direction rotation of the switching wheel, And a second switching rod provided in the second switching gear so as to be elastically approachable and confined to the second switching groove in correspondence to only one rotation of the switching wheel,
In a state where the first switching rod is constrained to the first switching groove, the first switching gear rotates by rotation of the switching wheel, and when the second switching rod is constrained to the second switching groove, And the second switching gear is rotated by rotation of the wheel. 5. The method of claim 4,
Wherein the first switching groove and the second switching groove are formed to have a gradually deeper depth from one end to the other end,
Wherein the first switching groove and the second switching groove are formed at one end with an entrance and at the other end with a step,
Wherein the first switching rod and the second switching rod are constrained at the step portion of the first switching groove and the second switching groove. The method according to claim 1,
The first shift fork unit includes:
A first gear engaged with the first switching gear; A first fork rod rotating together with the first gear; And a first fork connected to the synchronizer and linearly moving along the first fork rod in correspondence with the rotation of the first fork rod,
The second shift fork unit includes:
A second gear engaged with the second switching gear; A second fork rod rotating together with the second gear; And a second fork connected to the synchronizer and linearly moving along the second fork rod in correspondence with the rotation of the second fork rod. The method according to claim 6,
A first cam groove and a second cam groove are formed on outer circumferences of the first fork rod and the second fork rod,
Wherein the first fork and the second fork have first cam protrusions and second cam protrusions received in the first cam groove and the second cam groove,
The first fork moves linearly with respect to the first fork rod as the first cam protrusion moves along the first cam groove in correspondence with the rotation of the first fork rod,
And the second fork moves linearly with respect to the second fork rod as the second cam protrusion moves along the second cam groove in correspondence with the rotation of the second fork rod. The method according to claim 1,
The first shift fork unit includes:
A first gear engaged with the first switching gear; A first cam member having a first cam groove formed along an outer circumferential surface thereof and integrally coupled to a rotation shaft of the first gear and rotating together with the first gear; And a first fork connected to the synchronizer and moving along the first cam groove in correspondence to the rotation of the first cam member and linearly moving along the axial direction of the first cam member,
The second shift fork unit includes:
A second gear engaged with the second switching gear; A second cam member having a second cam groove formed along an outer circumferential surface thereof and integrally coupled to the rotation shaft of the second gear and rotating together with the second gear; And a second fork connected to the synchronizer and moving along the second cam groove corresponding to the rotation of the second cam member and linearly moving along the axial direction of the second cam member. Dual clutch transmission. The method according to claim 1,
Wherein the switch unit transmits the driving force of the driving motor to any one of the first shift fork unit and the second shift fork unit according to the rotation angle of the drive motor. 10. The method of claim 9,
Wherein said first shift fork unit includes a first barrel cam member for actuating a first fork mounted on a first fork rod adjacent said first counter shaft, And a second barrel cam member for actuating a second fork mounted on an adjacent second fork rod,
Wherein,
A first selector gear mounted on a shaft of the first barrel cam member, a second selector gear mounted on an axis of the second barrel cam member, and a second selector gear selectively transmitting power to either the first or second selector gear And a switching gear
Wherein the switching gear includes a gear surface meshed with the first and second select gears and a dovetail surface that is drivably separated from the first and second select gears,
And the first and second selection gears are exclusively connected to the switching gear. 11. The method of claim 10,
Wherein a stop value including a geneva gear surface is provided between gear teeth of the first and second selectable gears while a rotation of the first or second select gear while the geneva gear surface is in contact with the non- And the second clutch is engaged.

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