KR101603795B1 - Shifting Apparatus for Dual Clutch Transmission - Google Patents

Shifting Apparatus for Dual Clutch Transmission Download PDF

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Publication number
KR101603795B1
KR101603795B1 KR1020090087413A KR20090087413A KR101603795B1 KR 101603795 B1 KR101603795 B1 KR 101603795B1 KR 1020090087413 A KR1020090087413 A KR 1020090087413A KR 20090087413 A KR20090087413 A KR 20090087413A KR 101603795 B1 KR101603795 B1 KR 101603795B1
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KR
South Korea
Prior art keywords
shift
shaft
pin
cam
select
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Application number
KR1020090087413A
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Korean (ko)
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KR20110029644A (en
Inventor
김영광
Original Assignee
현대모비스 주식회사
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Priority to KR1020090087413A priority Critical patent/KR101603795B1/en
Publication of KR20110029644A publication Critical patent/KR20110029644A/en
Application granted granted Critical
Publication of KR101603795B1 publication Critical patent/KR101603795B1/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
    • 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
    • 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
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/32—Electric motors actuators or related electrical control means therefor
    • 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
    • F16H63/20—Multiple final output mechanisms being moved by a single common final actuating mechanism with preselection and subsequent movement of each final output mechanism by movement of the final actuating mechanism in two different ways, e.g. guided by a shift gate
    • 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
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/34—Locking or disabling mechanisms
    • F16H63/3408—Locking or disabling mechanisms the locking mechanism being moved by the final actuating mechanism
    • 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
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H2061/2892—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted other gears, e.g. worm gears, for transmitting rotary motion to the output mechanism
    • 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
    • F16H2063/025—Final output mechanisms for double clutch transmissions
    • 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
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H2063/3086—Shift head arrangements, e.g. forms or arrangements of shift heads for preselection or shifting

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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 simple structure, sufficient stiffness and durability, and provides a preselect function that permits shifting by shifting the engagement and disengagement states of two clutches while simultaneously engaging the other two speed change stages of the transmission system, It is possible to provide an active interlock function for preventing the two speed change stages of the same transmission system from being engaged at the same time, thereby ensuring reliable and stable operability.

DCT, shift, preselect, active interlock

Description

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

BACKGROUND OF THE INVENTION 1. Field of the Invention [0002] The present invention relates to a transmission device for a dual clutch transmission, and more particularly, to a technology for ensuring reliable and stable operability while permitting a structure of a speed change lug to be formed very simply.

The dual clutch transmission is constituted by two clutches unlike the conventional single plate clutch transmission system, in which the first clutch and the second clutch are designed as the transmission system designed to interlock the even-numbered gears, And it is also advantageous in that the fuel economy improvement effect can be obtained higher than that of the manual transmission vehicle.

Also, since the dual clutch transmission does not have an acceleration stop sensation generated in the single plate clutch, there is an advantage that the transmission feeling is also very excellent.

What is indispensable for controlling the above-described dual clutch transmission includes a clutch actuator for interrupting the clutch, a transmission for performing actual gear shifting by controlling a shift fork of the transmission, and a transmission for controlling such shift transmission according to the vehicle speed and the throttle valve opening degree or the like. There is a controller to control.

In this case, the transmission device not only merely shifts the gear, but also gears belonging respectively to the two speed-change systems divided into the odd-numbered and the even-numbered gears are shifted one by one and the shifting is effected only by switching the engagement and disengagement states of the two clutches Free select function to allow for

In addition, an active interlock function that keeps the shift lugs of the same transmission system not involved in the shift so as to prevent the two shift stages belonging to the same shift system from being engaged at the same time, should be provided in a neutral state.

Of course, the transmission needs to be able to provide the basic functions as described above with a simple structure and structure, to ensure its durability, and to ensure stable and reliable operability.

SUMMARY OF THE INVENTION The present invention has been devised in view of the above-described need, and it is an object of the present invention to provide a simple structure, sufficient rigidity and durability, and to achieve shifting by merely shifting the engagement and disengagement states of two clutches The present invention provides an active interlock function for preventing the two shift stages of the same transmission system from being engaged simultaneously at the same time and providing a reliable and stable operability, The present invention has been made in view of the above problems.

In order to achieve the above-mentioned object, the transmission of the dual clutch transmission according to the present invention,

A plurality of shift lugs arranged in overlapping relation so that each of the speed change stages is allocated and linearly movable in parallel with each other;

A shift shaft installed to be rotatable about a pivot axis along the direction of overlapping the speed change lugs and installed so as to be linearly movable along the pivot axis;

A shift pin formed radially to the shift shaft and linearly moving the shift lug;

A shift power transmission member which is concentric with the shift shaft and restrains rotation while permitting linear movement of the shift shaft in the axial direction and transmits the provided rotation force to the shift shaft;

A release shaft inserted into the shift shaft concentrically so as to be capable of rotating relative to the shift shaft, restraining axial linear movement, and having a plurality of release pins protruded in a radial direction;

An intermittent rotating means for rotating the release shaft at a predetermined angle smaller than the shift shaft by a rotational force transmitted from the shift power transmitting body;

Selecting means provided to linearly move the shift shaft in a direction of overlapping the shift lugs so as to select a shift lug to be operated by the shift pin;

And a control unit.

The present invention provides a simple structure, sufficient stiffness and durability, and provides a preselect function that permits shifting by shifting the engagement and disengagement states of two clutches while simultaneously engaging the other two speed change stages of the transmission system, It is possible to provide an active interlock function for preventing the two speed change stages of the same transmission system from being engaged at the same time, thereby ensuring reliable and stable operability.

1 to 10, the embodiment of the present invention includes a plurality of shift lugs 1 arranged in a superimposed manner so as to be linearly movable in parallel with each other, A shift shaft (3) rotatably mounted on a rotating shaft along a direction in which the speed change lugs (1) are stacked and installed so as to be linearly movable along the rotating shaft; A shift pin 5 protruding radially from the shift shaft 3 and linearly moving the shift lug 1; A shift power transmission body 7 concentric with the shift shaft 3 and restraining rotation while permitting linear movement of the shift shaft 3 in the axial direction and transmitting the provided rotational force to the shift shaft 3, Wow; A release shaft (3) having a plurality of release pins (9) protruded in a radial direction is inserted into the shift shaft (3) so as to be concentric with the shift shaft (3) 11); Intermittent rotation means for rotating the release shaft (11) at a predetermined angle smaller than the shift shaft (3) by a rotational force transmitted from the shift power transmission body (7); And a selecting means provided to linearly move the shift shaft 3 in the direction in which the shift lugs 1 are stacked so that the shift lug 1 to be operated by the shift pin 5 can be selected.

The shift pins 1 are inserted into the plurality of shift lugs 1 and are rotated so that the manipulation holes 13 having a simple rectangular shape for generating a linear sliding movement of the shift lug 1 have the same size So that the shifting pin 5 is moved in contact with the operating hole 13 of one of the shifting lugs 1 so that the shifting pin 5 is moved so that the shifting pin 1 is moved in the neutral position .

Hereinafter, two opposed surfaces constituting the operating hole 13, in which the shifting pin 5 is in contact with the shifting lug 1 and the shifting of the shifting lug 1 is performed, will be referred to as the operating surface 15. [ 7 and 8.

As shown in the drawing, the speed change lugs 1 are formed in substantially the same flat plate shape so as to be superposed on each other and easily aligned, and at least one speed change stage is assigned to both directions of linear movement. That is, referring to FIG. 9, there is a structure in which 1 & 3-speed lugs, 2 & 4-speed lugs, 5-speed lugs and 6 &

That is, the shifting lugs 1 of the odd-numbered-way shifting system and the even-numbered shifting-type shifting system are not adjacent to each other, but are arranged so as to be alternately superposed one after the other.

The shift shaft 3 is formed so that the shift pin 5 moves along the direction in which the shift lugs 1 are superimposed on each other As shown in FIG.

Therefore, the operation of shifting the shift pin 5 to one of the shift lugs 1 while the shift shaft 3 is moved up and down along the direction in which the shift lugs 1 are stacked is a selecting operation , The shifting operation is performed such that the shift pin 5 is linearly shifted to one side while the shift shaft 3 is rotated while the selection is performed as described above and the shift lug 1 The gears of the desired gear positions are engaged with each other.

The intermittent turning means includes an intermittent turning shaft 17 provided in parallel with the shift power transmitting body 7 and a cam driven shaft 17 integrally provided in the intermittent turning shaft 17 and opened toward the shift power transmitting body 7, (7) provided on the shift power transmission body (7) and inserted into the cam driven slot (19) of the driven cam plate (21), the shift power transmission body (7) A cam driving pin 23 for transmitting the rotational force of the driven cam plate 21 to the driven cam plate 21 when the cam driving pin 23 is pulled out from the cam driven slot 19, An intermittent drive pin 25 protruding from the intermittent rotary shaft 17 toward the release shaft 11 and an intermittent drive pin 25 interposed between the intermittent drive pin 25 and the release shaft 11, 11), while allowing the linear movement in the axial direction And a release driven slot (27) integrally provided in the release shaft (11) so that the release shaft (11) is rotated by a rotational force transmitted by the intermittent drive pin (25).

The rotation limiting cam means includes a projecting arcuate cam 29 projecting in an arcuate shape about the rotation shaft of the shift power transmission body 7 and an arc-shaped recess 29 formed in the driven cam plate 21 , A concave arcuate cam (31) whose surface of the arc surface of the projecting arcuate cam (29) is in surface contact with a line connecting the rotation shaft of the shift power transmission body (7) and the rotation shaft of the driven cam plate (21) .

The cam driving pin 23 and the cam driven slot 19 are located within a range of 36 degrees with respect to a straight line connecting the rotational shaft of the shift power transmitting body 7 and the rotational shaft of the driven cam plate 21, And the drive pin 23 is formed so as to be positioned in the cam driven slot 19. [

In this embodiment, the cam driving pin 23 is positioned within the range of 36 degrees with respect to the straight line connecting the rotation shaft of the shift power transmission body 7 and the rotation shaft of the driven cam plate 21, So that the driven cam plate 21 can be rotated, and the shift power transmitting body 7 itself can be further rotated to be rotated in the range of 72 degrees. 5 and 6.

As a result, while the shift power transmission body 7 is rotating in the range of 36 degrees with respect to the straight line connecting the rotation shaft of the shift power transmission body 7 and the rotation shaft of the driven cam plate 21, And the release shaft 11 via the intermittent rotary shaft 17 rotate equally at 36 degrees. However, only the shift power transmission body 7 and the shift shaft 3 And the intermittent rotation shaft 17 and the release shaft 11 are maintained in a state rotated to 36 degrees.

A plurality of release pins 9 protrude from the release shaft 11. The release pins 9 are protruded so as to be aligned with the speed change lugs 1 selected by the shift pins 5 and the other speed change lugs 1 of the same speed change system, . Therefore, in this embodiment, the shift pin 5 is shifted from the selected shift lug 1 in accordance with the disposition state of the respective shift lugs 1 of the alternately arranged odd-numbered shifting system and the even-numbered shifting system And is projected to act on the speed change lug 1 after skipping.

The selecting means includes a select motor 33, a select pin 35 having a rotational axis perpendicular to the axial direction of the shift shaft 3 and rotated by a rotational force from the select motor 33, The select pin 35 is inserted to allow a relative pivotal movement of the select pin 35 with the axial direction of the shift shaft 3 as a pivot axis and the axis of the shift pin 3 of the select pin 35 And includes a release bracket 11 and a select bracket 37 fixed to the shift shaft 3.

In the present embodiment, the select bracket 37 is fixed to the release shaft 11 and the shift shaft 3 integrally by a fixing pin 49. See FIG.

The select worm 39 is connected to the select motor 33 and the select pin 35 is integrally protruded from the select worm wheel 41 meshed with the select worm 39.

The shift power transmission body 7 is configured to receive a rotational force from a shift motor 43. A shift worm shaft 45 is connected to the shift motor 43. The shift power transmission body 7 receives the shift worm shaft 45, And a shift worm wheel 47 engaged with the shift worm wheel 45 are integrally provided.

Hereinafter, the operation of the embodiment of the present invention will be described.

When the select motor 33 is rotated, the select worm 39 rotates the select worm wheel 41 and the select pin 35 of the select worm wheel 41 moves the select bracket 37 up and down, As a result, the shift shaft 3 and the release shaft 11 fixed to the select bracket 37 are moved up and down together so that the shift pin 5 of the shift shaft 3 is displaced in a plurality of shift lugs 1, Or the like.

For example, FIG. 9 illustrates a process of selecting the 2 & 4-speed lug 1 from the state in which the shift pin 5 selects the 1 & 3-speed lug 1 in the selecting operation as described above.

When the shift motor 43 is driven in the above-described state, the shift worm wheel 47 is driven by the shift worm shaft 45 to rotate the shift power transmission body 7.

Since the rotation of the shift power transmission body 7 is directly transmitted to the shift shaft 3, the shift pin 5 is rotated together with the shift power transmission body 7, (1).

At this time, the rotational force of the shift power transmitting body 7 is transmitted to the intermittent rotating shaft 17 through the cam driving pin 23 and the cam driven slot 19, and the intermittent driving pin 17, (25) transmits a rotational force through the release driven slot (27), so that the release shaft (11) is rotated together with the shift shaft (3).

The rotation of the release shaft 11 is performed only within the range of 36 degrees in which the cam drive pin 23 is in the cam driven slot 19 and the cam drive pin 23 is moved in the cam driven slot 19 The cam driving pin 23 can not rotate the driven cam plate 21 and the driven cam plate 21 is depressed by the projecting arc cam 29 as the rotation limiting cam means The rotation of the arc-shaped cam 31 is suppressed by the mutual contact of the arc surfaces of the arc-shaped cam 31, and the rotation state is continuously maintained up to 36 degrees as described above.

The subsequent shift of the shift power transmission body 7 rotates the shift shaft 3 to a range of 72 degrees. The difference between the rotation range of the shift shaft 3 and the rotation range of the release shaft 11 is The shifting operation of the desired speed change stage is performed and the operation of the other speed change lug 1 in the same speed change system as the speed change stage in which the speed change is performed is limited, An active interlock function is implemented to prevent simultaneous coupling.

That is, when the release pin 9 rotated by the rotation of the release shaft 11 is rotated by 36 degrees, it touches the operation surface 15 of the shift lug 1 in the neutral state. The rotation of the shift shaft 3 continues to be maintained until 72 degrees so that the linear sliding of the shift lug 1 in the neutral state is restricted by the release pin 9, The linear sliding of the other speed change lug 1 belonging to the same speed change system as that of the speed change lug 1 contributing to the speed change is restricted by the shifting mechanism 5 and the two gears of the same speed change system are prevented from being engaged at the same time.

Of course, the shift pin 5 is further rotated from the remaining 36 degrees to the 72 degrees, so that the selected shift lug 1 is linearly moved so that the desired shift stages are engaged with each other.

10, the range of rotation of the shift pin 5 is limited to 72 degrees, the range of rotation of the release pin 9 is limited to 36 degrees, and in the state of 0 degrees of rotation, It is possible to move along the direction in which the shift lugs 1 are overlapped in the space provided by the shift lug 1 or between the shift lug 1 in the neutral state or all the shift lugs 1 in the respective operation holes 13 And a pre-select function for preliminarily matching the speed change gears of the different speed change system with the next high speed change possibility.

The transmission of the dual clutch transmission according to the present invention configured and operated as described above is not limited to the complex and precise shape of the speed change lug 1 as described above, but has a shape with only a simple rectangular operation hole 13 The speed change lug 1 can be easily machined, the manufacturing cost can be reduced, and there is no sharp shape that affects the operation, so that stable and reliable operation and long-term durable operation are possible.

In addition, as described above, the release shaft 9 and the release pin 9 for realizing the shift interlock with the shift shaft 3 and the shift pin 5 actually performing the shifting are separately provided with separate power transmission paths So that more reliable operability can be provided. In particular, even if wear of the components occurs, the homeostasis of various operations can be ensured.

1 is a view illustrating a transmission of a dual clutch transmission according to the present invention,

Fig. 2 is an exploded perspective view of Fig. 1,

3 is a sectional view taken along line III-III in Fig. 1,

4 is a sectional view taken along the line IV-IV in Fig. 1,

FIG. 5 is a view of another angle of FIG. 1,

FIG. 6 is a view for explaining the driving mechanism of the intermittently rotating shaft as a VI view in FIG. 5,

FIG. 7 is a view of the apparatus of FIG. 1 with the shift lugs in the state of being mounted on the housing,

8 is a view for explaining the structure of one shift lug,

FIG. 9 is a diagram sequentially illustrating the apparatus of FIG. 1 performing a selecting operation;

FIG. 10 is a diagram for explaining that the apparatus of FIG. 1 performs a shifting operation and an active interlock function.

BRIEF DESCRIPTION OF THE DRAWINGS FIG.

One; Shift lug 3; Shift shaft

5; Shift pin 7; Shift power train

9; Release pin 11; Release shaft

13; Operating hole 15; Operating surface

17; An intermittently rotating shaft 19; Cam driven slot

21; A driven cam plate 23; Cam drive pin

25; Intermittent drive pin 27; Release driven slot

29; A protruding arcuate cam 31; Recessed arc cam

33; Select motor 35; Select pin

37; Select bracket 39; Select Warm

41; Select worm wheel 43; Shift motor

45; Shift worm shaft 47; Shift worm wheel

49; Fixing pin

Claims (8)

A plurality of shift lugs arranged in overlapping relation so that each of the speed change stages is allocated and linearly movable in parallel with each other; A shift shaft installed to be rotatable about a pivot axis along the direction of overlapping the speed change lugs and installed so as to be linearly movable along the pivot axis; A shift pin formed radially to the shift shaft and linearly moving the shift lug; A shift power transmission member which is concentric with the shift shaft and restrains rotation while permitting linear movement of the shift shaft in the axial direction and transmits the provided rotation force to the shift shaft; A release shaft inserted into the shift shaft concentrically so as to be capable of rotating relative to the shift shaft, restraining axial linear movement, and having a plurality of release pins protruded in a radial direction; An intermittent rotating means for rotating the release shaft at a predetermined angle smaller than the shift shaft by a rotational force transmitted from the shift power transmitting body; Selecting means provided to linearly move the shift shaft in a direction of overlapping the shift lugs so as to select a shift lug to be operated by the shift pin; And the second clutch is engaged with the second clutch. [2] The apparatus according to claim 1, An intermittently rotating shaft provided parallel to the shift power transmission body; A driven cam plate provided integrally with the intermittently rotating shaft and having a cam driven slot opened toward the shift power transmission body; A cam driving pin provided on the shift power transmission body and adapted to transmit the rotational force of the shift power transmission body to the driven cam plate while being inserted into the cam driven slot of the driven cam plate; Rotation restricting cam means provided to limit the rotation of the driven cam plate when the cam driving pin is out of the cam driven slot; An intermittent drive pin protruding from the intermittent rotation shaft toward the release shaft; A release driven slot integrally formed with the release shaft such that the release shaft is rotated by a rotational force transmitted by the intermittent drive pin while allowing the intermittent drive pin to linearly move in the axial direction of the release shaft; And the second clutch is engaged with the second clutch. [3] The apparatus according to claim 2, A projecting arcuate cam protruding in an arcuate shape about the rotation shaft of the shift power transmission body; And a cam ring formed on the driven cam plate so as to be in a circular arc shape and having an arc surface between the protruding arcuate cams on a straight line connecting the rotational axis of the shift power transfer body and the rotational axis of the driven cam plate, cam; And the second clutch is engaged with the second clutch. The method of claim 3, The cam driving pin and the cam driven slot are formed such that the cam driving pin is positioned within the cam driven slot within a range of 36 degrees with respect to a straight line connecting the rotation shaft of the shift power transmission body and the rotation shaft of the driven cam plate that And the second clutch is engaged. 5. The apparatus according to any one of claims 1 to 4, wherein the selecting means A select motor; A select pin having a pivot axis perpendicular to an axial direction of the shift shaft and rotated by a rotational force from the select motor; Wherein the select pin is inserted to allow a relative pivoting motion in which the axis direction of the shift shaft of the select pin is a pivot axis and the relative linear movement along the axial direction of the shift shaft of the select pin is restricted, A select bracket fixed to the release shaft and the shift shaft; And the second clutch is engaged with the second clutch. The method of claim 5, A select worm is connected to the select motor; The select pin is formed integrally with the select worm wheel which is engaged with the select worm And the second clutch is engaged. The method according to any one of claims 1 to 4, The shift power transmission body is configured to receive a rotational force from a shift motor; A shift worm shaft is connected to the shift motor; The shift power transmission body includes a shift worm wheel integrated with the shift worm shaft And the second clutch is engaged. The method according to any one of claims 1 to 4, The shift lug is provided with an operation hole having a simple rectangular shape that causes the shift pin to be inserted and rotated so as to generate a linear sliding movement of the shift lug And the second clutch is engaged.
KR1020090087413A 2009-09-16 2009-09-16 Shifting Apparatus for Dual Clutch Transmission KR101603795B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020090087413A KR101603795B1 (en) 2009-09-16 2009-09-16 Shifting Apparatus for Dual Clutch Transmission

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Application Number Priority Date Filing Date Title
KR1020090087413A KR101603795B1 (en) 2009-09-16 2009-09-16 Shifting Apparatus for Dual Clutch Transmission

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KR101603795B1 true KR101603795B1 (en) 2016-03-17

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Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101039921B1 (en) 2009-07-28 2011-06-09 현대자동차주식회사 Shifting Apparatus for Double Clutch Transmission
CN106170647B (en) * 2014-04-02 2018-03-30 舍弗勒技术股份两合公司 hydraulic transmission actuator
DE102016205881A1 (en) * 2015-04-14 2016-10-20 Schaeffler Technologies AG & Co. KG Hydraulic gear actuator
KR101862471B1 (en) 2016-10-21 2018-05-29 현대다이모스(주) Actuator for dual clutch
FR3088400B1 (en) * 2018-11-08 2021-01-22 Renault Sas INTERNAL GEARBOX CONTROL SELECTION ACTUATOR

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020033059A1 (en) 2000-07-18 2002-03-21 Thomas Pels Gearbox
JP2008045664A (en) 2006-08-16 2008-02-28 Mitsubishi Fuso Truck & Bus Corp Transmission device
JP2008128465A (en) 2006-11-24 2008-06-05 Aisin Ai Co Ltd Operating device of transmission

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020033059A1 (en) 2000-07-18 2002-03-21 Thomas Pels Gearbox
JP2008045664A (en) 2006-08-16 2008-02-28 Mitsubishi Fuso Truck & Bus Corp Transmission device
JP2008128465A (en) 2006-11-24 2008-06-05 Aisin Ai Co Ltd Operating device of transmission

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