WO2014081198A1 - Transmission à double embrayage - Google Patents

Transmission à double embrayage Download PDF

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Publication number
WO2014081198A1
WO2014081198A1 PCT/KR2013/010576 KR2013010576W WO2014081198A1 WO 2014081198 A1 WO2014081198 A1 WO 2014081198A1 KR 2013010576 W KR2013010576 W KR 2013010576W WO 2014081198 A1 WO2014081198 A1 WO 2014081198A1
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WO
WIPO (PCT)
Prior art keywords
gear
switching
fork
rotation
shift
Prior art date
Application number
PCT/KR2013/010576
Other languages
English (en)
Korean (ko)
Inventor
강구태
추용주
Original Assignee
서강대학교 산학협력단
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from KR1020120131669A external-priority patent/KR102001552B1/ko
Priority claimed from KR1020120134777A external-priority patent/KR101568754B1/ko
Priority claimed from KR1020130007408A external-priority patent/KR101420700B1/ko
Application filed by 서강대학교 산학협력단 filed Critical 서강대학교 산학협력단
Publication of WO2014081198A1 publication Critical patent/WO2014081198A1/fr

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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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
    • F16H63/16—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism
    • F16H63/18—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism the final actuating mechanism comprising cams
    • 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
    • F16H63/304—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force
    • 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
    • F16H2061/2838—Arrangements with single drive motor for selecting and shifting movements, i.e. one motor used for generating both movements
    • 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
    • F16H63/304—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force
    • F16H2063/3056—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force using cam or crank gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths

Definitions

  • the present invention relates to a dual clutch transmission device, and more particularly, to a dual clutch transmission device that can simplify the structure and implement a simple shift.
  • the dual clutch transmission has two sets of clutches, in which one clutch is designed to form a separate transmission system that allows the clutch to engage a hole means gear and the other clutch to engage an even gear.
  • a shifting system it is widely used due to its advantages of easy operation, low power loss and fast shifting time.
  • the dual clutch transmission is shifted to the first to sixth stages, if the first clutch is traveling in the first stage, the second clutch is already waiting for the second stage to the second stage.
  • shifting starts the power of the first clutch is disconnected and the second clutch is connected.
  • the first clutch is shifted to the third gear by removing the first gear and waiting for the clutch to be connected 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.
  • the shift of the dual clutch transmission can be achieved by moving a shift fork holding a synchronizer disposed between gears of each stage to select a gear ratio of a desired gear stage.
  • the conventional shift fork is mounted to be linearly movable along the axial direction on a fork rod, and is interlocked by a barrel cam that is rotated by a driving motor and configured to linearly move.
  • Patent No. 10-1034890 discloses a shift device of a dual clutch transmission.
  • the shift device includes a first input shaft and a second input shaft connected to the first clutch and the second clutch, respectively, and two input shafts are suitably provided with drive gears for the first to seventh stages, and adjacent to the input shaft.
  • the counter shaft and the second counter shaft are provided with driven gears that engage the drive gears.
  • the shift fork includes a follow pin, which can position the shift fork in the right, left or middle position as the follow pin moves along the cam groove of the barrel cam.
  • the shifting device shifts gears from 1 to 7 gears, and shift forks of 5 gears and 7 gears are maintained in neutral (N) in the gear shifting gears from 1 gear to 3 gears.
  • the shift fork of the 1st to 3rd stage also maintains neutral (N) in the section.
  • the follower pin of the shift fork stops at an intermediate position of the cam groove, and generally stays in the rest period for about half of the entire circumference.
  • the long rest period means that the cam structure becomes complicated, which means that the diameter and weight of the barrel cam naturally increases because the slope of the shift section cannot be steeply formed in the cam groove of the barrel cam.
  • the increase in the diameter of the barrel cam can interfere with the compact design due to the large space of the barrel cam in the transmission, and the increase in weight means that as the moment of inertia of the barrel cam increases, fast and accurate control is difficult and the driving motor The disadvantage arises of the increased cost.
  • the present invention can simplify the structure, and provides a dual clutch transmission device that is easy to shift control.
  • the present invention provides a dual clutch transmission apparatus capable of controlling shifting using a single drive motor.
  • the present invention can reduce the cost, and provides a dual clutch transmission device that can improve the vehicle mountability.
  • a dual clutch transmission apparatus for implementing a shift by moving a synchronizer (synchronizer) in a dual clutch including a first counter shaft and a second counter shaft Is a first shift fork unit that shifts the synchronizer adjacent to the first countershaft to perform a shift operation, and a second shift fork unit that shifts 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 for selectively transmitting the driving force of the drive motor to any one of the first shift fork unit and the second shift fork unit.
  • the switch unit may be provided in various structures capable of selectively transferring the driving force of the driving motor to any one of the first shift fork unit and the second shift fork unit.
  • the switch unit may be configured to transmit 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 direction of the driving motor.
  • the switch unit is integrally coupled to the drive shaft of the drive motor is provided with a switching wheel that rotates together with the drive shaft, one side of the switching wheel so as to be idle with respect to the switching wheel, and with the switching wheel corresponding to only one direction rotation of the switching wheel.
  • the first shift fork unit may perform a shift operation in response to the rotation of the first switching gear
  • the second shift fork unit may perform a shift operation in response to the rotation of the second switching gear.
  • the first switch gear and the second switch gear are configured to be interlocked and rotated selectively by the switching wheel according to the rotational direction of the switching wheel.
  • An optional interlocking structure between the switching wheel and the first switch gear and the second switch gear is required.
  • 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 is provided to be elastically accessible to one surface of the switching wheel, so that the clockwise direction of the switching wheel is provided.
  • a first switching rod may be provided that is constrained to the first switching groove in correspondence only with rotation in either direction of rotation and counterclockwise rotation.
  • a second switching groove having a depth gradient along the circumferential direction may be formed on the other side of the switching wheel, and the second switching gear is provided to be elastically accessible to the other side of the switching wheel, so that the clock of the switching wheel may be
  • a second switching rod may be provided that is constrained to the second switching groove only in response to the rotation in the other direction during the directional rotation and the counterclockwise rotation.
  • 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 formed along the circumferential directions of the first switching gear and the second switching gear.
  • the switching groove has a progressively deep depth (or shallow depth) from one end to the other end.
  • One end of the first switching groove and the second switching groove may be formed with an entrance having a relatively shallow depth, and the other end may be formed with a stepped portion having a relatively deep depth, the first switching rod and the second switching rod
  • the first switching groove and the second switching groove may be restrained at the stepped portions.
  • an arc-shaped first switching groove may be formed on one surface of the switching wheel based on the first switch gear so as to have a deep depth gradually in the counterclockwise direction, and the other of the switching wheel based on the second switch gear.
  • An arc-shaped second switching groove may be formed on one surface to have a progressively deep depth along the counterclockwise direction.
  • the first shift fork unit and the second shift fork unit may be provided in various structures capable of a shift operation in response to rotation of the first switch gear and the second switch gear.
  • the first shift gear unit and the second shift fork unit perform a shift operation in response to the rotation of the first switch gear and the second switch gear. As it rotates, the first shift fork unit and the second shift fork unit are operated, and it can be understood that shifting is performed by moving the corresponding synchronizer.
  • the first shift fork unit is connected to a first gear engaged with the first switching gear, a first fork rod that rotates together with the first gear, and a synchronizer to rotate the first fork rod. It may be configured to include a first fork to linearly move along the first fork rod corresponding to the. In some cases, the first shift fork unit may be configured to include a cam member or a link member which may be interlocked by the rotation of the first switching gear. The first shift fork unit may be interlocked by the rotation of the first switching gear to straighten the synchronizer. It may also be of any other structure that can be moved.
  • the structure in which the first fork is interlocked by the rotation of the first fork rod may be variously changed according to required conditions and design specifications.
  • a first cam groove may be formed on an outer circumferential surface of the first fork rod, and a first cam protrusion accommodated in the first cam groove may be formed in the first fork, and the first fork may correspond to the rotation of the first fork rod.
  • the cam protrusion moves along the first cam groove, the first fork may move linearly with respect to the first fork rod.
  • the first fork may be linearly moved as the cam member is rotated by the rotation of the first fork rod by using a separate cam member.
  • One fork can be configured to work together.
  • the second shift fork unit is connected to the second gear gear meshed with the second switching gear, the second fork rod rotating together with the second gear, and the synchronizer, and the second fork rod corresponding to the rotation of the second fork rod. It may be configured to include a second fork that moves along the straight line. In some cases, the second shift fork unit may be configured to include a cam member or a link member which may be interlocked by the rotation of the second switching gear. The second shift fork unit may be interlocked by the rotation of the second switching gear and the synchronizer may be straight. It may also be of 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 may be variously changed according to required conditions and design specifications.
  • a second cam groove may be formed on an outer circumferential surface of the second fork rod, and a second cam protrusion may be formed in the second fork, and the second fork rod may correspond to the rotation of the second fork rod.
  • the cam protrusion moves along the second cam groove, the second fork may move linearly with respect to the second fork rod.
  • a separate cam member such as a barrel cam may be configured to rotate in response to the rotation of the first switch gear and the second switch gear, and the fork may be moved by the rotation of the cam member and configured to implement shifting.
  • the first shift fork unit the first gear is engaged with the first switching gear (engage), the first cam groove is formed along the outer peripheral surface is integrally coupled to the rotation axis of the first gear
  • a first cam member which rotates together with the first gear, and a first cam connected to the above-described synchronizer and moving along the first cam groove in response 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 may include a second gear engaged with the second switching gear and a second cam groove formed along an outer circumferential surface thereof and integrally coupled to the rotation shaft of the second gear to rotate together with the second gear. And a second fork connected to the second cam member and the synchronizer and moving along the second cam groove in response to the rotation of the second cam member and linearly moving along the axial direction of the second cam member.
  • the switch unit may be configured to transmit the driving force of the drive 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.
  • the first shift fork unit may include a first barrel cam member for operating a first fork mounted on a first fork rod adjacent to the first counter shaft
  • the second shift fork unit may include a second counter shaft. It may include a second barrel cam member for operating the second fork mounted to the second fork rod adjacent to the switch portion, the switch portion of the first selection gear, the second barrel cam member mounted to the shaft of the first barrel cam member A second selection gear mounted to the shaft, and a switching gear selectively transmitting power to any one of the first and second selection gears, wherein the first and second selection gears are exclusive of the switching gears. Can be connected.
  • a stop comprising a Geneva gear face may be provided between the gear teeth of the first and second select gears, wherein rotation of the first or second select gear during the interview with the Geneva gear face at the stop It may also be configured to be constrained.
  • the structure can be simplified and shift control is easy.
  • the driving force of the single drive motor is selectively provided by the switch unit without the need for separately providing a driving motor to operate the first shift fork unit and the second shift fork unit. And since it can be delivered to any one of the second shift fork unit, the structure can be simplified, and since only one motor needs to be controlled, shift control is more advantageous.
  • the synchronizer is linearly shifted and shifting can be implemented, thereby simplifying the structure and shifting control more easily. .
  • the shift fork can be directly moved in correspondence with the rotation of the fork rod, excluding a separate barrel cam member, the shift structure can be simplified, and shift control is more easily performed.
  • the shift is possible only by the fork rod and the shift fork, it can contribute to the miniaturization of the device, the cost can be reduced, and the vehicle mountability can be improved.
  • FIG. 1 is a view for explaining the configuration of a dual clutch transmission according to the present invention.
  • 2 to 4 is a view showing the structure of a dual clutch transmission according to the present invention.
  • 5 and 6 are views for explaining the operation structure of the dual clutch transmission according to the present invention.
  • FIG. 7 is a view showing the structure of a dual clutch transmission according to another embodiment of the present invention.
  • FIGS. 8 and 9 are diagrams for explaining a cam groove of the fork rod as a dual clutch transmission according to another embodiment of the present invention.
  • 10 to 12 are views showing the structure of a dual clutch transmission according to another embodiment of the present invention.
  • FIG. 13 is a view for explaining the configuration of a dual clutch transmission according to the present invention.
  • 16 is a diagram illustrating a switching gear and a selection gear as a dual clutch transmission according to the present invention.
  • FIG. 17 is a diagram illustrating a modified example of a switching gear and a selection gear as a dual clutch transmission according to the present invention.
  • 18 is a diagram for explaining a coupling structure between a fork rod and a fork as a dual clutch transmission according to the present invention.
  • 19 is a view for explaining the operating structure of the dual clutch transmission according to the present invention.
  • 20 is a diagram illustrating a dual clutch transmission according to another embodiment of the present invention.
  • 21 and 22 are diagrams for explaining a cam groove as a dual clutch transmission according to another embodiment of the present invention.
  • 23 is a view for explaining the configuration of the dual clutch transmission device according to the present invention.
  • 24 to 26 are views showing the structure of a dual clutch transmission according to the present invention.
  • 27 and 28 are diagrams for explaining the cam groove of the fork rod as a dual clutch transmission according to the present invention.
  • 29 is a diagram illustrating a dual clutch transmission according to another embodiment of the present invention.
  • FIG. 1 is a view for explaining the configuration of a dual clutch transmission according to the present invention
  • Figures 2 to 4 is a view showing the structure of a dual clutch transmission according to the present invention
  • Figures 5 and 6 the present invention
  • Figure 2 is a view for explaining the operation structure of the dual clutch transmission.
  • the dual clutch transmission device includes a gear shift portion and a shift portion.
  • the transmission gear unit includes a first clutch 11 and a second clutch 12 including a first clutch 11 and a second clutch 12, and a first input shaft 21 and a second input shaft 22 of the first and second clutches 11 and 12.
  • the rotational force generated in the engine may 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 may be transmitted to the first input shaft 21. ) Or to the second input shaft 22.
  • a 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.
  • 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 may be connected to the first clutch 11 to receive the rotational force generated by the engine.
  • the second input shaft 22 is disposed to overlap the same axis as the first input shaft 21, and may be connected to the second clutch 12 to receive a rotational force generated by the engine.
  • the second input shaft 22 may be formed in a hollow shape, 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 to be parallel to the first input shaft 21 and the second input shaft 22, and the first input shaft 21 and the second input shaft 22. Connected to receive the torque generated by the engine.
  • the plurality of drive 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, gear ratios. More specifically, the hole means drive gears D1, D3, D5, and D7 of the plurality of drive gears D1 to D8 may be connected to the first input shaft 21, and the pair of drive gears D2, D4, D6, and D8 may be connected to each other. ) 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 installed on the first counter shaft 23 and the second counter shaft 24, and have different gear ratios or transmission ratios, respectively.
  • the sixth driven gear G6 may be installed on the second counter shaft 24 without rotation interference
  • the gear G8 may be installed on the first counter shaft 23 without rotation interference.
  • 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 positioned between the corresponding driven gears G1, G2, G3, G4, G5, G6, G7, and G8.
  • the counter shaft 23 and the second counter shaft 24 are respectively provided.
  • the first synchronizer 31 is installed to be splined to the second counter shaft 24 so as to be located between the sixth driven gear G6 and the second driven gear G2, and the sixth driven It may be shifted by the second shift fork unit 320 to be described later to be fastened to the gear G6 or the second driven gear G2.
  • the second synchronizer 32 is disposed on one side of the first synchronizer 31 and is splined to the second counter shaft 24 so as to be positioned between the fifth driven gear G5 and the first driven gear G1. It may be installed so as to be shifted by the second shift fork unit 320 to be coupled to the fifth driven gear (G5) or the first driven gear (G1).
  • the third synchronizer 33 is disposed to face the first synchronizer 31, and is disposed on the first counter shaft 23 to be positioned between the eighth driven gear G8 and the fourth driven gear G4.
  • the spline may be shifted by the first shift fork unit 310 to be described later to be coupled to the eighth driven gear G8 or the fourth driven gear G4.
  • the fourth synchronizer 34 is disposed at one side of the third synchronizer 33 and is splined to the first counter shaft 23 so as to be positioned between the seventh driven gear G7 and the third driven gear G3. And shifted by the first shift fork unit 310 to be coupled to the seventh driven gear G7 or the third driven gear G3.
  • a conventional synchronizer may be used, and the present invention is not limited or limited by the type and characteristics of the synchronizer.
  • the sleeve of the synchronizer is coupled to the counter shaft by spline coupling, and is movable in the axial direction.
  • the synchronizer approaches and engages one of the driven gears, power can be transmitted through the engaged driven and drive gears, and the countershaft can transfer power through the other output shaft.
  • Specific structure of the synchronizer can refer to the conventional structure.
  • first to fourth sinks (31, 32, 33, 34), the first fork (316a, 316b) and the second fork (326a, 326b) of the first and second shift fork (310, 320), respectively Fastening grooves (not shown) for fastening may be formed, and the first to fourth synchronizers 31, 32, 33, and 34 are formed of the first forks 316a, 316b and the second forks 326a, 326b.
  • the shift unit is provided to shift the gear shift unit, and includes a first shift fork unit 310, a second shift fork unit 320, a drive motor 100, and a switch unit 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 countershaft 23, and the second shift fork unit 320 may be formed of a first shift fork unit 320.
  • the first shift fork unit 310 and the second shift fork unit 320 may be configured to move the synchronizers 31 and 32 adjacent to the second counter shaft 24 to perform a shift operation.
  • Various changes may be made depending on the conditions and 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.
  • a conventional motor may be used, and the present invention is not limited or limited by the type and characteristics of the motor. In some cases, other drive means such as solenoids may be used instead of the motor.
  • the switch unit 200 is configured to selectively transfer the driving force of the driving motor 100 to any one of the first shift fork unit 310 and the second shift fork unit 320, the first shift fork unit 310 And the second shift fork unit 320 may 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 in various structures capable of selectively transferring the driving force of the driving motor 100 to any one of the first shift fork unit 310 and the second shift fork unit 320.
  • the switch unit 200 may transmit the driving force of the driving motor 100 to any one of the first shift fork unit 310 and the second shift fork unit 320 according to the rotational direction of the driving motor 100. Can be configured.
  • the switch unit 200 is integrally coupled to the drive shaft of the drive motor 100 so as to rotate idling with respect to the switching wheel 230, the switching wheel 230 to rotate with the drive shaft.
  • the first switching gear 210 which is provided on one surface of the switching wheel 230 and rotates together with the switching wheel 230 in response to only one direction rotation of the switching wheel 230, and is capable of idling with respect to the switching wheel 230.
  • the first shift fork unit 310 may perform a shift operation in response to the rotation of the first switching gear 210, and the second shift fork unit 320 may correspond to the rotation of the second switching gear 220. To perform the shift operation.
  • the switching wheel 230 is provided between the first switching gear 210 and the second switching gear 220, is integrally coupled to the drive shaft of the drive motor 100 by the driving force by the drive motor 100 It can rotate clockwise or counterclockwise.
  • the first switching gear 210 is provided to rotate only in response to rotation of either the clockwise rotation or the counterclockwise rotation of the switching wheel 230.
  • the first switching gear 210 may be interlocked and rotated by the switching wheel 230 in response to only the clockwise rotation of the switching wheel 230, and the switching wheel 230 may rotate in the counterclockwise direction. In this case, the rotational force by the switching wheel 230 is not transmitted to the first switching gear 210, only the switching wheel 230 may rotate.
  • the second switching gear 220 is provided to rotate only in response to the rotation of the other direction of the clockwise rotation and the counterclockwise rotation of the switching wheel 230.
  • the second switching gear 220 may be interlocked and rotated by the switching wheel 230 in response to counterclockwise rotation of the switching wheel 230, and the switching wheel 230 may rotate in a clockwise direction.
  • the rotational force by the switching wheel 230 is not transmitted to the second switching gear 220, only the switching wheel 230 may rotate.
  • first switching gear 210 and the second switching gear 220 spur gears having teeth formed parallel to the axis along the outer circumferential surface may be used. However, in some cases, the first switching gear and the second switching gear may be used. Other gears may also be used.
  • the first switching gear 210 and the second switching gear 220 are configured to be interlocked and rotated by the switching wheel 230 selectively according to the rotation direction of the switching wheel 230, the first 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 configured to perform a shift operation.
  • the selective interlocking structure between the switching wheel 230, the first switching gear 210, and the second switching gear 220 may be variously changed according to required conditions and design specifications.
  • a 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 burnt on one surface of the switching wheel 230.
  • a first switching rod 212 is provided that is sexually accessible and is constrained to the first switching groove 232 in response to only one of the clockwise rotation and the counterclockwise rotation of the switching wheel 230. Can be.
  • 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 on the other surface of the switching wheel 230 on the second switching gear 220.
  • a second switching rod 222 which is provided to be elastically accessible and constrained to the second switching groove 234 in correspondence with the rotation of the other direction of the clockwise rotation and the counterclockwise rotation of the switching wheel 230 is provided. Can be provided.
  • the first switching rod 212 and the second switching rod 222 are supported by the common spring members 214 and 224 and elastically contact the corresponding first switching gear 210 and the second switching gear 220. Can be. In some cases, other elastic members may be used instead of the spring members, and the present invention is not limited or limited by the elastic support structures of the first switching rod and the second switching rod.
  • first switching groove 232 and the second switching groove 234 have a depth gradient along the circumferential direction, the circumference 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 may be understood to have a progressively deep depth (or shallow depth) from one end to the other end. Entry portions 232a and 234a having a relatively shallow depth may be formed at one end of the first switching groove 232 and the second switching groove 234 and a stepped portion 232b having a relatively deep depth at the other end thereof.
  • first switching rod 212 and the second switching rod 222 are restrained at the stepped portions 232b and 234b of the first switching groove 232 and the second switching groove 234.
  • an arc-shaped first switching groove 232 may be formed on one surface of the switching wheel 230 based on the first switching gear 210 so as to have a deep depth gradually in a counterclockwise direction.
  • the second switching groove 234 having an arc shape may be formed on the other surface of the switching wheel 230 based on the switching gear 220 to have a deep depth gradually along the counterclockwise direction.
  • the switching wheel 230 when the switching wheel 230 rotates in the clockwise direction, the first switching rod 212 may be constrained to the stepped portion 232b of the first switching groove 232, and the first switching may be performed. Due to the constraint between the rod 212 and the first switching groove 232, the switching wheel 230 may also interlock with the first switching gear 210 in a clockwise direction and rotate in a clockwise direction. In addition, when the switching wheel 230 rotates in the clockwise direction, since the second switching rod 222 moves from the stepped portion 234b of the second switching groove 234 in the direction of the entry portion 234a, the switching is performed. The rotational force of the wheel is not transmitted to the second switching gear 220.
  • the second switching rod 222 may be constrained to the stepped portion 234b of the second switching groove 234, and the second switching rod ( By the restraint between the 222 and the second switching groove 234, the switching wheel 230 is also interlocked corresponding to the counterclockwise direction, the second switching gear 220 may also be interlocked and rotate in the counterclockwise direction.
  • the switching wheel 230 rotates in the counterclockwise direction, since the first switching rod 212 moves from the step portion 232b of the first switching groove 232 toward the entry portion 232a, 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 in various structures capable of shift operation in response to rotation of the first switching gear 210 and the second switching gear 220. Can be.
  • the first shifting gear unit and the second shifting fork unit perform a shift operation in response to the rotation of the first switching gear and the second switching gear. As it rotates, the first shift fork unit and the second shift fork unit are operated, and it can be understood that shifting is performed by moving the corresponding synchronizer.
  • the first shift fork unit 310 has a first gear 210 engaged with the first switching gear 210 and a first fork rod 314 rotating together with the first gear 210. ) And a first fork connected to the above-described synchronizer (see 33 and 34 of FIG. 1) and linearly moving along the first fork rod 314 in response to the rotation of the first fork rod 314. 316a, 316b).
  • the first shift fork unit may be configured to include a cam member or a link member which may be interlocked by the rotation of the first switching gear.
  • the first shift fork unit may be interlocked by the rotation of the first switching gear to straighten the synchronizer. It may also be of any other structure that can be moved.
  • the first gear 210 may be interlocked and rotated as the first switching gear 210 rotates, and the first gear 210 may be splined to the first gear 210 as the first gear 210 rotates.
  • the fork rod 314 may rotate together, and the first forks 316a and 316b may linearly move along the first fork rod 314 by the rotation of the first fork rod 314.
  • a first cam groove 314a is formed on an 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.
  • the first fork rods 314 are formed as the first cam protrusion 317 moves along the first cam groove 314a in response to the rotation of the first fork rod 314.
  • the first fork is straight as the cam member rotates by the rotation of the first fork rod using a separate cam member.
  • the first fork may be configured to interlock by rotating the first fork rod in another structure.
  • the first cam protrusion 317 may be circulated and moved along the first cam groove 314a as the first fork rod 314 rotates, and the angle and the structure of the first cam groove 314a are required conditions and design. It may be changed according to specifications.
  • the gear ratio between the first switching gear 210 and the first gear 210 may be appropriately changed according to the required conditions and design specifications. For example, when the first switching gear 210 rotates 1/2, the first gear 210 may be configured to rotate once.
  • the second shift fork unit 320 includes a second gear 220 engaged with the second switching gear 220, a second fork rod 324 rotating together with the second gear 220, and a synchronizer ( And second forks 326a and 326b linearly moving along the second fork rod 324 in response to the rotation of the second fork rod 324.
  • the second shift fork unit may be configured to include a cam member or a link member which may be interlocked by the rotation of the second switching gear.
  • the second shift fork unit may be interlocked by the rotation of the second switching gear and the synchronizer may be straight. It may also be of any other structure that can be moved.
  • first shift fork unit and the second shift fork unit have been described with an example having the same structure. However, in some cases, the first shift fork unit and the second shift fork unit are different from each other. It may be of other structure.
  • the second gear 220 may be interlocked and rotated as the second switching gear 220 rotates, and the second gear 220 may be splined to the second gear 220 as the second gear 220 rotates.
  • the fork rod 324 may rotate together, and the second forks 326a and 326b may linearly move along the second fork rod 324 by the rotation of the second fork rod 324.
  • a second cam groove 324a is formed on the outer circumferential surface of the second fork rod 324, and the second cam protrusion 327 accommodated in the second cam groove 324a is formed in the second forks 326a and 326b.
  • the second fork rods 324a and 326b are formed as the second cam protrusion 327 moves along the second cam groove 324a in response to the rotation of the second fork rod 324.
  • An example configured to move linearly with respect to the second fork may be linearly moved as the cam member is rotated by the rotation of the second fork rod by using a separate cam member. Two forks can be configured to work together.
  • the second cam protrusion 327 may 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 are required conditions and design. It may be changed according to specifications.
  • the gear ratio between the second switching gear 220 and the second gear 220 may be appropriately changed according to the required conditions and design specifications. For example, when the second switching gear 220 rotates 1/2, the second gear 220 may be configured to rotate once.
  • the first switching gear 210 switches the switching wheel 230 as the first switching rod 212 is constrained to the first switching groove 232. It is linked by and rotates clockwise.
  • the first switching gear 210 rotates, the first fork rod 314 may rotate while the first gear 210 meshed with the first switching gear 210 rotates, and the first fork rod 314 may rotate.
  • the switching wheel 230 rotates in the clockwise direction, since the rotational force by the switching wheel 230 is not transmitted to the second switching gear 220, the second switching gear 220 is connected to the switching wheel 230. To idle.
  • the second switching gear 220 switches the switching wheel 230.
  • the second fork rod 324 may rotate while the second gear 220 engaged with the second switching gear 220 rotates, and the second fork rod 324 may rotate.
  • the switching wheel 230 rotates in the counterclockwise direction, since the rotational force by the switching wheel 230 is not transmitted to the first switching gear 210, the first switching gear 210 is the switching wheel 230. Will idle against.
  • Figure 7 is a view showing a dual clutch transmission according to another embodiment of the present invention.
  • the same or equivalent reference numerals are given to the same or equivalent components as those described above, and detailed description thereof will be omitted.
  • the dual clutch transmission device includes a driving wheel 100, a switching wheel 230 that is integrally coupled to a driving shaft of the driving motor 100 and rotates together with the driving shaft.
  • a first switching gear 210 which is provided on one surface of the switching wheel 230 so as to be idling with respect to the switching wheel 230 and rotates together with the switching wheel 230 in response to only one direction rotation of the switching wheel 230;
  • the second switching gear 220 is provided on the other surface of the switching wheel 230 so as to be idling with respect to the switching wheel 230 and rotates together with the switching wheel 230 in response to only one rotation of the other direction of the switching wheel 230.
  • a first shift fork unit 310 ′ that performs a shift operation by moving a synchronizer (see 31 to 34 of FIG. 1) in response to the rotation of the first switching gear 210, and the first shift gear unit 310 ′.
  • 2 Shift the synchronizer in response to the rotation of the switching gear 220
  • a second shift fork unit 320 ′ wherein the first shift fork unit 310 ′ includes: a first gear 312 ′ engaged with the first switching gear 210; A first cam member 318 'is formed along the outer circumference and integrally coupled to the rotation shaft 314' of the first gear 312 'to rotate together with the first gear 312'.
  • a first unit connected to the above-described synchronizer and moving along the first cam groove 318a 'in response to the rotation of the first cam member 318' and linearly moving along the axial direction of the first cam member 318 '. It may be configured to include one fork (316a ', 316b'), the second shift fork unit 320 ', the second gear 322' engaged with the second switching gear 220 (engage).
  • the second cam groove 328 ' is formed along the outer circumference and is integrally coupled to the rotation shaft 324' of the second gear 322 'to rotate together with the second gear 322'. ), And connected to the synchronizer to counteract the rotation of the second cam member 328 '.
  • the second fork 326a 'and 326b may move along the second cam groove 328a' and linearly move along the axial direction of the second cam member 328 '.
  • the profiles of the first cam groove 318a 'and the second cam groove 328a' may be appropriately changed according to the required conditions and design specifications, and the present invention may be achieved by the profiles of the first cam groove and the second cam groove. It is not limited or limited.
  • the first cam groove 318a 'and the second cam groove 328a' have both end portions formed on the outer surfaces of the first cam member 318 'and the second cam member 328'.
  • the first forks 316a 'and 316b' and the second forks 326a 'and 326b may be formed as the first cam member 318' and the second cam member 328 'are rotated.
  • the cam groove 318a 'and the second cam groove 328a' may be circulated and moved.
  • both ends of the first cam groove and the second cam groove are connected to each other, in some cases, both ends of the first cam groove and the second cam groove may be separated.
  • the first cam groove 318a ′′ (or the second cam groove) may provide a path in which both ends thereof are separated.
  • both ends of the first cam groove and the second cam groove may be provided.
  • the synchronizer may be moved to a desired position while the first cam member and the second cam member are rotated forward or reversely.
  • the first cam groove (or the second cam groove) may be separated from both ends of the first cam member.
  • the angle 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 formed longer within the range where the first cam grooves do not overlap each other.
  • the first cam member and the second cam member is provided with a single cam groove May be provided.
  • the first switching rod (see 212 of FIG. 3) is constrained to the first switching groove (see 232 of FIG. 3).
  • 210 is interlocked by the switching wheel 230 and rotates in a clockwise direction.
  • the first cam member 318 ' may rotate while the first gear 312' engaged with the first switching gear 210 rotates, and the first cam member is rotated.
  • 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 '. Shifting can be done by moving the Niger.
  • the switching wheel 230 rotates in the clockwise direction, since the rotational force by the switching wheel 230 is not transmitted to the second switching gear 220, the second switching gear 220 is connected to the switching wheel 230. To idle.
  • the switching wheel 230 rotates in the counterclockwise direction, as the second switching rod (see 222 of FIG. 3) is constrained to the second switching groove (see 234 of FIG. 3), the second switching gear 220 is rotated. It is interlocked by the switching wheel 230 and rotates in the counterclockwise direction.
  • the second cam member 328 ' may rotate while the second gear 322' engaged with the second switching gear 220 rotates, and the second cam member may rotate.
  • the second forks 326a 'and 326b' move along the second cam grooves 328a 'in response to the rotation of 328' and move in a straight line along the axial direction of the second cam member 328 '.
  • Shifting can be done by moving the Niger.
  • the switching wheel 230 rotates in the counterclockwise direction, since the rotational force by the switching wheel 230 is not transmitted to the first switching gear 210, the first switching gear 210 is the switching wheel 230. Will idle against.
  • Figures 10 to 12 is a view showing the structure of a dual clutch transmission device according to another embodiment of the present invention.
  • the same or equivalent reference numerals are given to the same or equivalent components as those described above, and detailed description thereof will be omitted.
  • the switch unit may be configured to transmit the driving force of the drive 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.
  • the first shift fork unit 1310 may include a first for operating the first forks 326a and 326b mounted to the first fork rod 324 adjacent to the first counter shaft (see 24 in FIG. 1).
  • a barrel cam member 1250 may be included, and the second shift fork unit 1320 may be a second fork 316a mounted to a second fork rod 314 adjacent to a second counter shaft (see 23 of FIG. 1).
  • the switch portion 1200 is the first selection gear 1210, the second mounted on the shaft of the first barrel cam member 1250
  • FIG. 10 is a view for explaining a cam driving unit of a transmission apparatus according to still another embodiment of the present invention
  • FIG. 11 is a side view for explaining the switch unit of FIG. 10.
  • the transmission includes a driving motor 100 and a switch unit 1200, and optionally, the first barrel cam member 1250 or the second using the switch unit 1200.
  • the barrel cam member 1240 may be rotated.
  • the contents of selectively operating the first barrel cam member 1250 or the second barrel cam member 1240 according to the rotation angle by using the gearless gear is not partially formed,
  • a switch unit for selectively operating some of the two or more barrel cam members according to the rotation direction such as a one-way clutch, may be provided.
  • the cam driver includes one of the driving motor 100 and the first and second barrel cam members 1250 and 1240 for the first and second barrel cam members 1250 and 1240. It includes a switch unit 1200 for transmitting power of the drive motor 100 to one, the switch unit 1200 is the first selection gear 1210, the second barrel mounted on the shaft of the first barrel cam member 1250 The second selection gear 1220 mounted on the shaft of the cam member 1240, and the switching gear 1230 disposed between the first and second selection gears 1210 and 1220.
  • the switching gear 1230 is formed with a gear tooth at an angle of about 180 degrees, and a gear tooth is deleted at an opposite 180 degree angle. Accordingly, the first selection gear 1210 may be engaged at 180 degrees, and the second selection gear 1220 may be engaged at an opposite rotation of 180 degrees.
  • the switching gear 1230 includes a gear surface and an inclined surface.
  • the switching gear 1230 may be engaged with the first or second selection gears 1210 and 1230 by the gear surface, and is driven separately from the first or second selection gears 1210 and 1230 by the gearless surface. State can be achieved.
  • the driving separated state may include a state in which power cannot be transmitted even in a state in which physical power is separated and cannot transmit power.
  • the first and second selection gears 1210 and 1220 may be exclusively connected to the switching gear 1230 by the combination of the gear surface and the toothless surface. In some cases, it may form a section that moves together.
  • FIG. 12 is a side view for explaining a switch unit of a transmission device according to another embodiment of the present invention similar to the switch unit of FIG. 11.
  • the switching unit 1230 ′ disposed between the first selection gear 1210 ′, the second selection gear 1220 ′, and the first and second selection gears 1210 ′ and 1220 ′. ) May be included.
  • the switching gear 1230 ′ provides a gear face on which the gear tooth is formed at an angle of about 180 degrees and a chamfered surface with the gear tooth removed at the opposite 180 degree angle.
  • the first selection gear 1210 ′ and the second selection gear 1220 ′ may further include stop values 1212 ′ and 1222 ′ including at least one Geneva gear surface between the gear teeth. Gene and gear surfaces of the stop values 1212 'and 1222' remain in contact with the chamfered surface, so that the first or second selector gears 1210 'and 1220' will not shake even if power is cut off from the chamfered surface. Rotation can be constrained to maintain state.
  • FIG. 13 is a view for explaining the configuration of the dual clutch transmission according to the present invention
  • Figures 14 and 15 are views showing the structure of the dual clutch transmission according to the present invention
  • Figure 16 is a view of the present invention
  • Figure 17 is a dual clutch transmission according to the invention, a view for explaining a variation of the switching gear and the selection gear
  • Figure 18 is a dual clutch transmission according to the present invention
  • a coupling structure between the fork rod and the fork 19 is a view for explaining the operation structure of the dual clutch transmission according to the present invention.
  • the dual clutch transmission device includes a transmission gear part and a shift part.
  • the transmission gear unit includes a first clutch 11 and a second clutch 12 including a first clutch 11 and a second clutch 12, and a first input shaft 21 and a second input shaft 22 of the first and second clutches 11 and 12.
  • the rotational force generated in the engine may 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 may be transmitted to the first input shaft 21. ) Or to the second input shaft 22.
  • a 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.
  • 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 may be connected to the first clutch 11 to receive the rotational force generated by the engine.
  • the second input shaft 22 is disposed to overlap the same axis as the first input shaft 21, and may be connected to the second clutch 12 to receive a rotational force generated by the engine.
  • the second input shaft 22 may be formed in a hollow shape, 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 to be parallel to the first input shaft 21 and the second input shaft 22, and the first input shaft 21 and the second input shaft 22. Connected to receive the torque generated by the engine.
  • the plurality of drive 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, gear ratios. More specifically, the hole means drive gears D1, D3, D5, and D7 of the plurality of drive gears D1 to D8 may be connected to the first input shaft 21, and the pair of drive gears D2, D4, D6, and D8 may be connected to each other. ) 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 installed on the first counter shaft 23 and the second counter shaft 24, and have different gear ratios or transmission ratios, respectively.
  • the sixth driven gear G6 may be installed on the second counter shaft 24 without rotation interference
  • the gear G8 may be installed on the first counter shaft 23 without rotation interference.
  • 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 positioned between the corresponding driven gears G1, G2, G3, G4, G5, G6, G7, and G8.
  • the counter shaft 23 and the second counter shaft 24 are respectively provided.
  • the first synchronizer 31 is installed to be splined to the second counter shaft 24 so as to be located between the sixth driven gear G6 and the second driven gear G2, and the sixth driven It may be shifted by the second shift fork unit 3320 to be described later to be fastened to the gear G6 or the second driven gear G2.
  • the second synchronizer 32 is disposed on one side of the first synchronizer 31 and is splined to the second counter shaft 24 so as to be positioned between the fifth driven gear G5 and the first driven gear G1. It may be installed to be shifted by the second shift fork unit 3320 to be fastened to the fifth driven gear (G5) or the first driven gear (G1).
  • the third synchronizer 33 is disposed to face the first synchronizer 31, and is disposed on the first counter shaft 23 to be positioned between the eighth driven gear G8 and the fourth driven gear G4.
  • the spline may be shifted by the first shift fork unit 3310 to be described later to be coupled to the eighth driven gear G8 or the fourth driven gear G4.
  • the fourth synchronizer 34 is disposed at one side of the third synchronizer 33 and is splined to the first counter shaft 23 so as to be positioned between the seventh driven gear G7 and the third driven gear G3. And shifted by the first shift fork unit 3310 to be coupled to the seventh driven gear G7 or the third driven gear G3.
  • a conventional synchronizer may be used, and the present invention is not limited or limited by the type and characteristics of the synchronizer.
  • the sleeve of the synchronizer is coupled to the counter shaft by spline coupling, and is movable in the axial direction.
  • the synchronizer approaches and engages one of the driven gears, power can be transmitted through the engaged driven and drive gears, and the countershaft can transfer power through the other output shaft.
  • Specific structure of the synchronizer can refer to the conventional structure.
  • first to fourth sinks 31, 32, 33, and 34 have first and second forks 3316a, 3316b, and second forks 3326a, 3162a, of the first and second shift fork units 3310, 3320, respectively.
  • a fastening groove (not shown) for fastening the 3326b may be formed, and the first to fourth sinkers 31, 32, 33, and 34 may have a first fork 3316a, 3316b and a second fork 3326a.
  • the rotation of the driven gears G1, G2, G3, G4, G5, G6, G7, G8 is synchronized to the first counter shaft 23 or the second counter shaft 24 by moving in the axial direction by the .3326b). To be possible.
  • the shift unit is provided to shift the gear shift unit, and includes a driving motor 3110, a switching gear 3120, a first selection gear 3130, a second selection gear 3140, and a first shift fork unit 3310. And a second shift fork unit 3320, and a driving force of the driving motor 3110 with any one of the first shift fork unit 3310 and the second shift fork unit 3320 according to the rotation angle of the driving motor 3110. This can be delivered.
  • the drive motor 3110 provides a driving force for rotating the switching gear 3120 to be described later. Only one single motor may be used as the driving motor 3110, and the present invention is not limited or limited by the type and characteristics of the motor.
  • the switching gear 3120 is provided between the first selection gear 3130 and the first selection gear 3130, which will be described later, and is integrally coupled to the driving shaft of the driving motor 3110 to drive the driving force by the driving motor 3110. Can be rotated clockwise or counterclockwise.
  • the first selection gear 3130 is provided to be meshed with the gear surface of the switching gear 3120 in accordance with the rotation angle of the switching gear 3120, and selectively switching gears corresponding to the rotation angle of the switching gear 3120 ( 3120 is provided to rotate together.
  • the second selection gear 3140 is provided to be meshed with the gear surface of the switching gear 3120 according to another rotation angle of the switching gear 3120, and selectively switches to correspond to another rotation angle of the switching gear 3120. It is provided to rotate with the gear 3120.
  • spur gears having teeth formed parallel to the axis along the outer circumferential surface thereof may be used, but in some cases, the first selection gear and the second selection gear may be used. Other gears may also be used.
  • a gear surface 3122 is formed on a part of the circumferential surface of the switching gear 3120, and a valueless surface 3124 is formed on the remaining part of the circumferential surface.
  • the switching gear 3120 is formed with a gear tooth at an angle of about 180 degrees, and a gear tooth is deleted at an opposite 180 degree angle. Therefore, the first selection gear 3130 may be engaged at 180 degrees, and the second selection gear 3140 may be engaged at an opposite 180 degrees.
  • the switching gear 3120 may engage with the first or second selection gears 3130 and 3140 by the gear surface 3122, and the first or second selection gear by the solid surface 3124. 3130 and 3140 may be driven and separated from each other.
  • the driving separated state may include a state in which power cannot be transmitted even in a state in which physical power is separated and cannot transmit power.
  • the first and second selection gears 3130 and 3140 may be exclusively connected to the switching gear 3120 by a combination of the gear surface and the toothless surface. In some cases, it may form a section that moves together.
  • FIG. 17 is a diagram illustrating a modified example of the switching gear and the selection gear as the dual clutch transmission according to the present invention.
  • the same or equivalent reference numerals are given to the same or equivalent components as those described above, and detailed description thereof will be omitted.
  • the shift unit 3120 ' is disposed between the first selection gear 3130', the second selection gear 3140 ', and the first and second selection gears 3130' and 3140 '. ) May be included.
  • the switching gear 3120 ' provides a gear face on which the gear teeth are formed at an angle of about 180 degrees and a chamfered surface with gear teeth removed at the opposite 180 degrees angle.
  • first selection gear 3130 ′ and the second selection gear 3140 ′ may further include stop values 3132 ′ and 3142 ′ including at least one Geneva gear surface between the gear teeth.
  • stop values 3132 ′ and 3142 ′ remain in an interview with the chamfered surface, so that power is cut off from the chamfered surface of the first selector gear 3130 ′ or the second selector gear 3140 ′.
  • the rotation can be constrained so that it remains steady without being shaken.
  • the first shift fork unit 3310 and the second shift fork unit 3320 may have various structures capable of shifting in response to rotation of the first selection gear 3130 and the second selection gear 3140. It may be provided as.
  • the first shift fork unit 3310 and the second shift fork unit 3320 perform a shift operation in response to the rotation of the first selection gear 3130 and the second selection gear 3140.
  • the first selection gear 130 and the second selection gear 3140 rotate, the first shift fork unit 3310 and the second shift fork unit 3320 operate and correspond to the synchronizers 31 to 34. It can be understood that shifting is achieved by moving.
  • the first shift fork unit 3310 may include a first fork rod 3314 rotating together with the first selection gear 3130, and the above-described synchronizer (see 33 and 34 of FIG. 13).
  • the first fork 3316a and 3316b connected to each other and linearly moving along the first fork rod 3314 may correspond to the rotation of the first fork rod 3314.
  • the first shift fork unit may be configured to include a cam member or a link member that can be interlocked by the rotation of the first selection gear. It may also be of any other structure that can be moved.
  • the first fork rod 3314 coupled to the first selection gear 3130 in a spline manner may rotate together with the rotation of the first fork rod 3314.
  • the first forks 3316a and 316b may linearly move along the first fork rod 3314.
  • a first cam groove 3314a is formed on an outer circumferential surface of the first fork rod 3314, and a first cam protrusion 3317 accommodated in the first cam groove 3314a is formed in the first forks 3316a and 3316b.
  • the first fork 3316a and 3316b are formed as the first cam protrusion 3317 moves along the first cam groove 3314a in response to the rotation of the first fork rod 3314.
  • An example configured to move linearly with respect to In some cases, the first fork may be linearly moved as the cam member is rotated by the rotation of the first fork rod by using a separate cam member.
  • One fork can be configured to work together.
  • the first cam protrusion 3317 may be circulated and moved along the first cam groove 3314a as the first fork rod 3314 rotates, and an angle and a structure of the first cam groove 3314a may be required. It may be changed according to specifications.
  • the second shift fork unit 3320 is connected to the second fork rod 3324 and the synchronizer (see FIGS. 31 and 32 of FIG. 13) which rotate together with the second selection gear 3140, and the second fork rod 3324. It may include a second fork (3326a, 326b) that moves linearly along the second fork (3324) corresponding to the rotation of the).
  • the second shift fork unit may be configured to include a cam member or a link member that can be interlocked by the rotation of the second selection gear. It may also be of any other structure that can be moved.
  • the first shift fork unit and the second shift fork unit have been described with an example having the same structure. However, in some cases, the first shift fork unit and the second shift fork unit are different from each other. It may be of other structure.
  • the second fork rod 3324 coupled to the second selection gear 3140 in a spline manner may rotate together with the rotation of the second fork rod 3324.
  • the second forks 3326a and 3326b may linearly move along the second fork rod 3324.
  • a second cam groove 3324a is formed on the outer circumferential surface of the second fork rod 3324, and a second cam protrusion 3327 accommodated in the second cam groove 3324a is formed in the second forks 3326a and 3326b.
  • the second fork 3326a and 3326b are formed as the second cam protrusion 3327 moves along the second cam groove 3324a in response to the rotation of the second fork rod 3324.
  • An example configured to move linearly with respect to In some cases, the second fork may be linearly moved as the cam member is rotated by the rotation of the second fork rod by using a separate cam member. Two forks can be configured to work together.
  • the second cam protrusion 3327 can be circulated and moved along the second cam groove 3324a as the second fork rod 3324 rotates, and the angle and structure of the second cam groove 3324a are required conditions and design. It may be changed according to specifications.
  • the above-described embodiment of the present invention has been described with an example in which both ends of the first cam groove and the second cam groove of the first fork rod and the second fork rod are connected, but in some cases, the first cam groove and Both ends of the second cam groove may be formed in a separated form.
  • the synchronizer in a manner in which both ends of the first cam groove and the second cam groove are separated, the synchronizer can be moved to a desired position while the first fork rod and the second fork rod are rotated forward or reverse.
  • the gear surface 3122 of the switching gear 3120 is engaged with the first selection gear 3130 or the second selection gear 3140 in response to the rotation angle of the switching gear 3120.
  • the selection gear 3130 or the second selection gear 3140 is interlocked by the switching gear 3120 to rotate.
  • the first fork rod 3314 or the second fork rod (314) connected to the first selection gear 3130 or the second selection gear 3140 ( 3324 may rotate.
  • the first cam protrusions 3317 move along the first cam grooves 3314a in response to the rotation of the first fork rods 3314
  • the first forks 3316a and 3316b may move relative to the first fork rods 3314.
  • the second cam protrusion 3327 moves along the second cam groove 3324 a in response to the rotation of the second fork rod 3324.
  • the second forks 3326a and 3326b may linearly move with respect to the second fork rod 3324 to move the corresponding synchronizer to implement shifting.
  • the rotational force of the switching gear 3120 is selected by the first selection gear 3130 or the second selection gear. Since it is not transmitted to the gear 3140, the first selection gear 3130 or the second selection gear 3140 does not rotate even if the switching gear 3120 rotates.
  • FIGS. 21 and 22 are views illustrating a cam groove as a dual clutch transmission according to another embodiment of the present invention.
  • the same or equivalent reference numerals are given to the same or equivalent components as those described above, and detailed description thereof will be omitted.
  • a driving motor 3110 a gear surface is formed on a part of the circumferential surface, and a non-gear surface is formed on the remaining part of the circumferential surface
  • the drive motor Switching gear 3120 rotated by 3110, the first selection gear which is provided to engage the gear surface and selectively rotates with the switching gear 3120 in response to the rotation angle of the switching gear (3120) 3130, a second selection gear 3140 that is provided to be meshed with the gear surface and selectively rotates with the switching gear 3120 in response to the rotation angle of the switching gear 3120, and the first selection gear 3130.
  • a first shift fork unit 3310 ′ that shifts the synchronizer (see 33 and 34 in FIG. 13) adjacent to the first counter shaft (see 23 in FIG. 13) in response to the rotation of And a second count corresponding to the rotation of the second selection gear 140.
  • a second shift fork unit 3320 ' that moves the synchronizer (see 31, 32 of FIG. 13) adjacent to the shaft (see 24 of FIG. 13) to perform a shift operation, the first shift fork unit 3310 ') Is a first barrel cam is formed along the outer circumferential surface of the first cam cam 3318a' is integrally coupled to the rotating shaft (3132 ') of the first selection gear (3130) and rotates together with the first selection gear (3130).
  • a first fork 3316a 'and 3316b' linearly moving along the direction, and the second shift fork unit 3320 ' has a second cam groove 3328a' formed along an outer circumferential surface thereof.
  • a second barrel cam member 3328 ' that is integrally coupled to the rotation shaft 3314' of the second selection gear 3140 and rotates together with the second selection gear 140, and is connected to the synchronizer A second fork 3326a 'and 3326b moving along the second cam groove 3328a' in response to the rotation of the barrel cam member 3328 'and linearly moving along the axial direction of the second barrel cam member 3328'.
  • the profiles of the first cam grooves 3318a 'and the second cam grooves 3328a' may be appropriately changed according to required conditions and design specifications, and the present invention may be modified by the profiles of the first cam grooves and the second cam grooves. It is not limited or limited.
  • both ends of the first cam groove 3318a 'and the second cam groove 3328a' are formed at the outer surfaces of the first barrel cam member 3318 'and the second barrel cam member 3328'.
  • the first interlock pin (not shown) and the second interlock pin (not shown) connected to the first barrel cam member 3318 'and the second barrel cam member 3328' may be formed in a continuous shape.
  • the cam member 3318 'and the second barrel cam member 3328' rotate, the cam member 3318 'and the second barrel cam member 3328' can be circulated and moved along the corresponding first cam groove 3318a 'and the second cam groove 3328a'.
  • both ends of the first cam groove and the second cam groove are formed in a continuous form
  • both ends of the first cam groove and the second cam groove are formed in a separated form. It is also possible.
  • the first cam groove (3318a ") and the second cam groove (not shown) may provide a path that is separated at both ends.
  • the first cam groove 3318a" and the second cam groove in one direction. Only moving is blocked at the end, and it must be rotated in the opposite direction to bring the synchronizer close to the right or left.
  • the switching gear 3120 may move the first interlock pin and the second interlock pin to a desired position while forward or reverse rotation of the first barrel cam member 3318 'and the second barrel cam member 3328'. Can be.
  • the first cam grooves 3318a "and the second cam grooves are 360 degrees or more in an angle range formed at the outer surfaces of the first barrel cam member 3318 'and the second barrel cam member 3328' instead of both ends thereof being separated.
  • the length of the first cam groove 3318a may be longer than the first cam groove 3318a" (or the second cam groove) does not overlap each other.
  • the first cam groove 3318a "(or the second cam groove) does not overlap each other.
  • the cam groove 3318a is the first cam groove 3318a in a longer path or larger angle range in the first barrel cam member 3318 'of the same diameter as compared to the first cam groove 3318a' shown in FIG. ") Can be formed.
  • the slope of the inclined section for changing the position of the first interlock pin connected to the first fork 3316a, 3316b in the first cam groove (3318a ") (or the second cam groove) can be formed more gently, Interference can be kept to a minimum, and the speed of the shift can be further increased. That is, the first cam groove 3318a "(or second cam groove) structure of FIG. 22 has an independent first barrel cam member for each counter shaft. 3318 ') and the second barrel cam member 3328', and as a result, a sufficient cam groove path can be secured even at a small diameter, so that the first barrel cam member 3318 'and the second barrel cam member 3328 can be obtained.
  • the smaller diameter of the ') can bring many technical advantages such as miniaturization and light weight, fast rotation and accurate control, and reduction of the cost of the driving motor 3110.
  • first barrel cam member and the second barrel cam member are described with an example configured to have the same diameter or thickness in the embodiment of the present invention, in some cases, the first barrel cam member and the second barrel cam member. May be configured to have different diameters or thicknesses, and a portion where the first cam groove and the second cam groove are formed in the first barrel cam member and the second barrel cam member has a relatively larger diameter or larger thickness than other portions. It is also possible to be formed to have.
  • a plurality of cam grooves are formed in the first barrel cam member and the second barrel cam member, but in some cases, the first barrel cam member and the second barrel cam member are single cam grooves. It may be provided with a plurality.
  • the gear surface of the switching gear 3120 is engaged with the first selection gear 3130 or the second selection gear 3140 in response to the rotation angle of the switching gear 3120.
  • the first barrel cam member 3318 'or the second barrel cam member may rotate.
  • the first forks 3316a' and 3316b ' move along the first cam groove 3318a' and along the axial direction of the first barrel cam member 3318 '.
  • the corresponding synchronizer can be moved to implement a shift
  • the second fork 3326a 'and 3326b' correspond to the rotation of the second barrel cam member 3328 '.
  • the corresponding synchronizer can be moved to implement shifting.
  • the rotational force of the switching gear 3120 is selected by the first selection gear 3130 or the second selection gear. Since it is not transmitted to the gear 3140, the first selection gear 3130 or the second selection gear 3140 does not rotate even if the switching gear 3120 rotates.
  • Figure 23 is a view for explaining the configuration of the dual clutch transmission device according to the present invention
  • Figures 24 to 26 is a view showing the structure of the dual clutch transmission device according to the present invention
  • Figures 27 and 28 As a dual clutch transmission according to the present invention, it is a view for explaining the cam groove of the fork rod.
  • the dual clutch transmission apparatus includes a gear shift portion and a shift portion.
  • the transmission gear unit includes a first clutch 11 and a second clutch 12 including a first clutch 11 and a second clutch 12, and a first input shaft 21 and a second input shaft 22 of the first and second clutches 11 and 12.
  • the rotational force generated in the engine may 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 may be transmitted to the first input shaft 21. ) Or to the second input shaft 22.
  • a 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.
  • 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 may be connected to the first clutch 11 to receive the rotational force generated by the engine.
  • the second input shaft 22 is disposed to overlap with the first input shaft 21 on the same axis, and is connected to the second clutch 12 to receive the rotational force generated by the engine.
  • the second input shaft 22 may be formed in a hollow shape, 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 to be parallel to the first input shaft 21 and the second input shaft 22, and the first input shaft 21 and the second input shaft 22. Connected to receive the torque generated by the engine.
  • the plurality of drive 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, gear ratios.
  • the hole means drive gears D1, D3, D5, and D7 of the plurality of drive gears D1 to D8 may be connected to the first input shaft 21, and the pair of drive gears D2, D4, D6, and D8 may be used.
  • the plurality of driven gears G1, G2, G3, G4, G5, G6, G7, and G8 are respectively installed on the first counter shaft 23 and the second counter shaft 24, and have different gear ratios or transmission ratios, respectively.
  • the sixth driven gear G6 may be installed on the second counter shaft 24 without rotation interference
  • the gear G8 may be installed on the first counter shaft 23 without rotation interference.
  • 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 positioned between the corresponding driven gears G1, G2, G3, G4, G5, G6, G7, and G8.
  • the counter shaft 23 and the second counter shaft 24 are respectively provided.
  • the first synchronizer 31 is installed to be splined to the second counter shaft 24 so as to be located between the sixth driven gear G6 and the second driven gear G2, and the sixth driven It may be shifted by the second shift fork unit 4320 to be described later to be fastened to the gear G6 or the second driven gear G2.
  • the second synchronizer 32 is disposed on one side of the first synchronizer 31 and is splined to the second counter shaft 24 so as to be positioned between the fifth driven gear G5 and the first driven gear G1. It may be installed to be shifted by the second shift fork (4320) to be fastened to the fifth driven gear (G5) or the first driven gear (G1).
  • the third synchronizer 33 is disposed to face the first synchronizer 31, and is disposed on the first counter shaft 23 to be positioned between the eighth driven gear G8 and the fourth driven gear G4.
  • the spline may be shifted by the first shift fork unit 4310 to be described later to be coupled to the eighth driven gear G8 or the fourth driven gear G4.
  • the fourth synchronizer 34 is disposed at one side of the third synchronizer 33 and is splined to the first counter shaft 23 so as to be positioned between the seventh driven gear G7 and the third driven gear G3.
  • the first shift fork unit 4310 may be shifted to be coupled to the seventh driven gear G7 or the third driven gear G3.
  • a conventional synchronizer may be used, and the present invention is not limited or limited by the type and characteristics of the synchronizer.
  • the sleeve of the synchronizer is coupled to the counter shaft by spline coupling, and is movable in the axial direction.
  • the synchronizer approaches and engages one of the driven gears, power can be transmitted through the engaged driven and drive gears, and the countershaft can transfer power through the other output shaft.
  • Specific structure of the synchronizer can refer to the conventional structure.
  • first to fourth shift synchronizers 31, 32, 33, and 34 may include first and second shift forks 4316a and 4316b and second shift forks of the first and second shift fork units 4310 and 4320, respectively.
  • a fastening groove (not shown) for fastening the 4326a and 4326b may be formed, and the first to fourth sinkers 31, 32, 33, and 34 may include the first shift forks 4316a and 316b and the second.
  • the shift unit may be provided to shift the shift gear unit, and may include a first shift fork unit 4310 and a second shift fork unit 4320.
  • first shift fork unit 4310 and the second shift fork unit 4320 have the same structure will be described.
  • first shift fork unit and the second shift fork unit may have different structures.
  • only one shift fork unit may be used, and the present invention is not limited or limited by the number of shift fork units.
  • the first shift fork unit 4310 may be provided to move the synchronizers 34 and 33 commonly associated with the first counter shaft 23, and include a first driving motor 4312 and the first driving motor.
  • the first fork rod 4314 rotates by 4312 and the synchronizers 34 and 33 and linearly moves along the first fork rod 4314 in response to the rotation of the first fork rod 4314.
  • first shift forks 4316a and 4316b are provided to move the synchronizers 34 and 33 commonly associated with the first counter shaft 23, and include a first driving motor 4312 and the first driving motor.
  • the synchronizer commonly associated with the first counter shaft 23 may be understood as the synchronizers 34 and 33 for shifting driven gears installed in the first counter shaft 23.
  • the first driving motor 4312 provides a driving force for rotating the first fork rod 4314 to be described later.
  • a general motor may be used as the first driving motor 4312, and the present invention is not limited or limited by the type and characteristics of the first driving motor 4312.
  • other driving means such as a solenoid may be used as the driving unit for providing a driving force for rotating the first fork rod instead of the first driving motor.
  • the first shift forks 4316a and 4316b are connected to the synchronizers 34 and 33 associated with the first counter shaft 23, and the first fork rods 4314 correspond to the rotation of the first fork rods 4314.
  • the first shift forks 4316a and 4316b are linearly moved in response to the rotation of the first fork rod 4314.
  • the synchronizer associated with the first counter shaft 23 34 and 33 are linearly moved and shifting can be implemented.
  • the structure in which the first shift forks 4316a and 4316b linearly move along the first fork rod 4314 due to the rotation of the first fork rod 4314 may be variously changed according to required conditions and design specifications.
  • a first cam groove 4314a may be formed on an outer circumferential surface of the first fork rod 4314 and a first cam protrusion accommodated in the first cam groove 4314a in the first shift forks 4316a and 4316b. 4317 may be formed.
  • the first shift forks 4316a and 4316b May linearly move relative to the first fork rod 4314.
  • the first cam groove is formed on the outer circumferential surface of the first fork rod, and the first cam protrusion is formed on the first shift fork. It is also possible to form a first cam projection on the outer circumferential surface and to form a first cam groove on the first shift fork.
  • the first cam groove 4314a may be formed in a form in which both ends thereof are connected to the outer surface of the first fork rod 4314, and the first cam protrusion 4317 may be the first fork rod. As the 4314 rotates, the 4320 may be circulated along the first cam groove 4314a and move.
  • the angle and structure of the first cam groove 4314a may be appropriately changed according to required conditions and design specifications, and the present invention is not limited or limited by the angle and structure of the first cam groove 4314a. .
  • the second shift fork unit 4320 may be provided to move a synchronizer commonly associated with the second counter shaft 24, and may be provided by the second driving motor 4322 and the second driving motor 4322.
  • Second fork rods 4324 rotating and second shift forks 4326a and 4326b connected to the synchronizer and linearly moving along the second fork rods 4324 corresponding to the rotation of the second fork rods 4324. It is configured to include.
  • the synchronizer commonly associated with the second counter shaft 24 may be understood as a synchronizer for shifting driven gears installed in the second counter shaft 24.
  • the second driving motor 4322 provides a driving force for rotating the second fork rod 4324.
  • a general motor may be used as the second driving motor 4322, and the present invention is not limited or limited by the type and characteristics of the second driving motor 4322.
  • other driving means such as solenoids may be used as the driving unit for providing the driving force for rotating the second fork rod instead of the second driving motor.
  • the second shift forks 4326a and 4326b are connected to a synchronizer associated with the second countershaft 24 and move linearly along the second fork rod 4324 in response to the rotation of the second fork rod 4324. As the second shift forks 4326a and 4326b are linearly moved in response to the rotation of the second fork rod 4324, the synchronizer associated with the second counter shaft 24 is linearly moved and shifting is performed. Can be implemented.
  • the structure in which the second shift forks 4326a and 4326b are linearly moved along the second fork rod 4324 by the rotation of the second fork rod 4324 may be variously changed according to required conditions and design specifications.
  • a second cam groove 4324a may be formed on an outer circumferential surface of the second fork rod 4324, and a second cam protrusion accommodated in the second cam groove 4324a may be formed in the second shift forks 4326a and 4326b.
  • 4227 may be formed and second shift forks 4326a and 4326b move as the second cam protrusion 4327 moves along the second cam groove 4324a in response to the rotation of the second fork rod 4324. May linearly move relative to the second fork rod 4324.
  • the second cam groove 4324a may be formed in a form in which both ends thereof are connected to the outer surface of the first fork rod 4314, and the second cam protrusion 4327 may be formed in the second fork rod.
  • the 4320 may be circulated and moved along the second cam groove 4324a.
  • the angle and structure of the second cam groove 4324a may be appropriately changed according to required conditions and design specifications, and the present invention is not limited or limited by the angle and structure of the second cam groove 4324a. .
  • both ends of the first cam groove and the second cam groove are formed is described, but in some cases, both ends of the first cam groove and the second cam groove are separated. It is also possible to form.
  • the first cam groove 4314a ′′ (or the second cam groove) may provide a broken path at both ends thereof.
  • the first cam groove 4314a ′′ (or the second cam groove) may be disposed in one direction. Only moving is blocked at the end, and it must be rotated in the opposite direction to bring the synchronizer close to the right or left.
  • the first driving motor 4312 (or the second driving motor) is connected to the first shift forks 4316a and 4316b (or the second shift fork) while the first fork rod 4314 rotates forward or reverse.
  • the interlock pin (not shown) may be moved to a desired position.
  • the first cam groove 4314a ′′ (or the second cam groove) may extend the angle range formed at the outer surface of the first fork rod 4314 to 360 degrees or more, instead of being separated at both ends, and the first cam groove ( The length of the first cam groove 4314a "can be formed longer within the range where the 4314a") do not overlap each other.
  • the first cam groove 4314a "in FIG. 28 is the first cam groove 4314a shown in FIG.
  • the first cam groove 4314a can be formed in a longer path or a larger angle range in the first fork rod 4314 of the same diameter.
  • the slope of the inclined section for changing the position of the interlock pins connected to the first shift forks 4316a and 4316b in the first cam groove 4314a may be formed more gently, so that interference is kept to a minimum when shifting. It is also possible to increase the speed of the shift more quickly, that is, the structure of the first cam groove 4314a "(or the second cam groove) of FIG. 28 is possible by the first fork rod 4314 (or the second fork rod). As a result, since a sufficient cam groove path can be secured even at a small diameter of the first fork rod 4314, there is no need to increase the diameter of the fork rod, and the fork rod can be made smaller and lighter, faster rotation, and accurate control. It can bring many technical advantages such as lower driving motor cost.
  • FIG. 25 illustrates an example in which the first fork rod 4314 and the second fork rod 4324 have the same diameter or thickness as a whole, but in some cases, the first fork rod may be the same as in FIG. 26.
  • the portion where the first cam groove 4314a and the second cam groove 4324a are formed in the 4314 and the second fork rod 4324 may be formed to have a relatively large diameter or a larger thickness than other portions.
  • first fork rod and the second fork rod are described as examples configured to be driven by separate drive motors, but in some cases, the driving force by one drive motor It is also possible to be configured to be selectively delivered to the first fork rod or the second fork rod by this separate switching means.
  • Figure 29 is a view showing a dual clutch transmission according to another embodiment of the present invention.
  • the same or equivalent reference numerals are given to the same or equivalent components as those described above, and detailed description thereof will be omitted.
  • a dual clutch transmission apparatus may include a fork rod 4314 ′ that is rotated by driving motors 4312 ′ and 4322 ′ and the driving motors 4312 ′ and 4322 ′. 4324 ', and shift forks 4316a' connected to the synchronizers 31 to 34 and linearly moving along the fork rods 4314 'and 4324' in response to rotation of the fork rods 4314 'and 4324'. 4316b ', 4326a', and 4326b ', wherein the fork rods 4314' and 4324 'may be provided in plurality in correspondence with the synchronizers 31 to 34 associated with specific countershafts 23 and 24.
  • the shift forks 4316a ', 4316b', 4326a ', and 4326b' may be independently provided to the fork rods 4314 'and 4324', respectively, and the driving motors 4312 'and 4322' may be provided to the fork rods.
  • 4314 'and 4324' may be provided to correspond to each other to drive the fork rods 4314 'and 4324' independently.
  • first fork rods 4314 ′ constituting the first shift fork unit 4310 ′ may be provided to be spaced apart from each other at predetermined intervals, and each of the first fork rods 4314 ′ may be provided with a first fork rod 4314 ′.
  • the shift forks 4316a 'and 4316b' may be provided one by one, and each of the first fork rods 4314 'may be independently driven by different first driving motors 4312'.
  • two second fork rods 4324 'constituting the second shift fork unit 4320' may be provided with two spaced apart at predetermined intervals, and each second fork rod 4324 'has a second shift.
  • Forks 4326a 'and 4326b' may be provided one by one, and each of the second fork rods 4324 'may be independently driven by different second driving motors 4322'.
  • first shift forks 4316a 'and 4316b' provided to each of the first fork rods 4314 ' may be connected to the synchronizers 34 and 33 commonly associated with the first counter shaft 23.
  • the second shift forks 4326a 'and 4326b' provided to each of the second fork rods 4324 ' may be connected to synchronizers 32 and 31 which are commonly associated with the second counter shaft 24.
  • the plurality of first fork rods 4314 ′ may be coaxially or non-coaxially disposed with each other, and likewise, the plurality of second fork rods 4324 ′ may also be coaxially or non-coaxially disposed with each other.
  • first fork rods 4314 ′ are coaxially arranged with each other and a plurality of second fork rods 4324 ′ are arranged coaxially with each other will be described.
  • three or more fork rods may be used, and each fork rod may be disposed to be inclined with each other.
  • cam grooves may be formed on the outer circumferential surfaces of the first fork rod 4314 ′ and the second fork rod 4324 ′, and corresponding shift forks ( 4316a ', 4316b', 4326a ', and 4326b' may be formed with a cam protrusion (see 4317 in FIG. 29) accommodated in the cam groove, and the first fork rod 4314 'and the second fork rod 4324' may be formed.

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

Abstract

La présente invention porte sur une transmission à double embrayage présentant une structure simplifiée permettant de changer facilement de vitesse. Selon l'invention, une transmission à double embrayage permettant de changer de vitesse par le déplacement d'un synchroniseur dans un double embrayage comprenant un premier arbre intermédiaire et un second arbre intermédiaire comprend : une première unité formant fourchette de débrayage destinée à exécuter une opération de changement de vitesse par le déplacement d'un synchroniseur adjacent au premier arbre intermédiaire ; une seconde unité formant fourchette de débrayage destinée à exécuter une opération de changement de vitesse par le déplacement d'un synchroniseur adjacent au second arbre intermédiaire ; un moteur d'entraînement destiné à appliquer une force d'entraînement afin d'entraîner les première et seconde unités formant fourchette de débrayage ; et une pièce de commutation destinée à transférer de manière sélective la force d'entraînement du moteur d'entraînement à l'une desdites première et seconde fourchettes de débrayage.
PCT/KR2013/010576 2012-11-20 2013-11-20 Transmission à double embrayage WO2014081198A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
KR1020120131669A KR102001552B1 (ko) 2012-11-20 2012-11-20 듀얼클러치 변속장치
KR10-2012-0131669 2012-11-20
KR1020120134777A KR101568754B1 (ko) 2012-11-26 2012-11-26 듀얼클러치 변속장치
KR10-2012-0134777 2012-11-26
KR10-2013-0007408 2013-01-23
KR1020130007408A KR101420700B1 (ko) 2013-01-23 2013-01-23 듀얼클러치 변속장치

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WO2014081198A1 true WO2014081198A1 (fr) 2014-05-30

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PCT/KR2013/010576 WO2014081198A1 (fr) 2012-11-20 2013-11-20 Transmission à double embrayage

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WO (1) WO2014081198A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201700045182A1 (it) * 2017-04-26 2018-10-26 Indemar Ind Spa Sistema di comando di una unità di azionamento
US10337610B2 (en) 2015-11-25 2019-07-02 Hyundai Dymos Incorporated Gear actuator for dual clutch transmission

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008304025A (ja) * 2007-06-11 2008-12-18 Mitsubishi Motors Corp 変速装置
EP1965102B1 (fr) * 2007-03-01 2010-04-14 C.R.F. Società Consortile per Azioni Dispositif de commande de changement de vitesses servo-assisté pour transmission à embrayage double de véhicule à moteur
JP2010127388A (ja) * 2008-11-27 2010-06-10 Mitsubishi Motors Corp 自動変速機の変速操作装置
US20110048150A1 (en) * 2008-03-13 2011-03-03 Zf Friedrichshafen Ag Actuating assembly for a centrally syncronised dual-clutch transmission
KR101095719B1 (ko) * 2008-12-11 2011-12-21 현대모비스 주식회사 듀얼클러치 변속기의 변속장치

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1965102B1 (fr) * 2007-03-01 2010-04-14 C.R.F. Società Consortile per Azioni Dispositif de commande de changement de vitesses servo-assisté pour transmission à embrayage double de véhicule à moteur
JP2008304025A (ja) * 2007-06-11 2008-12-18 Mitsubishi Motors Corp 変速装置
US20110048150A1 (en) * 2008-03-13 2011-03-03 Zf Friedrichshafen Ag Actuating assembly for a centrally syncronised dual-clutch transmission
JP2010127388A (ja) * 2008-11-27 2010-06-10 Mitsubishi Motors Corp 自動変速機の変速操作装置
KR101095719B1 (ko) * 2008-12-11 2011-12-21 현대모비스 주식회사 듀얼클러치 변속기의 변속장치

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10337610B2 (en) 2015-11-25 2019-07-02 Hyundai Dymos Incorporated Gear actuator for dual clutch transmission
DE102016223018B4 (de) * 2015-11-25 2019-07-25 Hyundai Dymos Incorporated Getriebezahnradbetätigungseinrichtung für ein doppelkupplungsgetriebe
IT201700045182A1 (it) * 2017-04-26 2018-10-26 Indemar Ind Spa Sistema di comando di una unità di azionamento

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