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WO2014116028A1 - Transmission à double embrayage - Google Patents

Transmission à double embrayage Download PDF

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Publication number
WO2014116028A1
WO2014116028A1 PCT/KR2014/000635 KR2014000635W WO2014116028A1 WO 2014116028 A1 WO2014116028 A1 WO 2014116028A1 KR 2014000635 W KR2014000635 W KR 2014000635W WO 2014116028 A1 WO2014116028 A1 WO 2014116028A1
Authority
WO
WIPO (PCT)
Prior art keywords
fork
cam
cam groove
fork rod
shift
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/KR2014/000635
Other languages
English (en)
Korean (ko)
Inventor
강구태
추용주
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Industry University Cooperation Foundation of Sogang University
Original Assignee
Industry University Cooperation Foundation of Sogang University
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 KR1020130007408A external-priority patent/KR101420700B1/ko
Priority claimed from KR1020130007413A external-priority patent/KR101390339B1/ko
Application filed by Industry University Cooperation Foundation of Sogang University filed Critical Industry University Cooperation Foundation of Sogang University
Publication of WO2014116028A1 publication Critical patent/WO2014116028A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F16H63/24—Final output mechanisms therefor; Actuating means for the final output mechanisms each of the final output mechanisms being moved by only one of the various final actuating mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
    • 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
    • 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 parallel flow paths, e.g. dual 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/32—Electric motors , actuators or related electrical control means  therefor

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 made by moving the shift fork member holding the synchronizer disposed between the gears of each stage to select the gear ratio of the desired gear stage.
  • the existing shift fork member 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 member includes a follow pin, and the follow pin may move along the cam groove of the barrel cam to position the shift fork member in a right, left or intermediate position.
  • the shifting device shifts gears from 1 to 7 gears, and the shift fork members of 5 gears and 7 gears maintain a neutral (N) in the section shifting from 1 gear to 3 gears.
  • the shift fork members 1 to 3 in the shifting section also maintain the neutral (N). That is, when one barrel cam is used, the follow pin of the shift fork member stops at an intermediate position of the cam groove, and generally stays about half of the entire circumference in the resting period.
  • 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
  • the first shift fork unit including a first cam element and a first fork member which moves in correspondence with the rotation of the first cam element and moves the synchronizer adjacent to the first counter shaft to perform a shift operation.
  • a second shift fork unit including a second cam element and a second fork member which moves in correspondence with the rotation of the second cam element and moves the synchronizer adjacent to the second counter shaft to perform a shift operation;
  • a driving unit for simultaneously rotating the first cam element and the second cam element.
  • the first shift fork unit may be provided in various structures capable of performing a shift operation by moving the synchronizer adjacent to the first counter shaft, and the second shift fork unit moves by shifting the synchronizer adjacent to the second counter shaft. It may be provided in various structures capable of performing an operation. For reference, in the present invention, that the first shift fork unit and the second shift fork unit perform the shift operation, and the first shift fork unit and the second shift fork unit are operated by the driving force of the driving unit and correspond to the corresponding synchronizer. It can be understood that shifting takes place.
  • first cam element of the first shift fork unit and the second cam element of the second shift fork unit various cam members capable of converting rotational motion into linear motions of the first fork member and the second fork member may be used.
  • the structure and characteristics of the cam element and the second cam element can be variously changed according to the required conditions and design specifications.
  • the first cam element includes a first barrel cam member having a first cam groove formed along an outer circumferential surface, and the first fork member moves along the first cam groove in response to the rotation of the first barrel cam member.
  • the second cam element includes a second barrel cam member having a second cam groove formed along an outer circumferential surface thereof, and the second fork member is formed in response to the rotation of the second barrel cam member. 2 may move along the groove and linearly move along the axial direction of the second barrel cam member, the first barrel cam member and the second barrel cam member may be rotated at the same time by the drive unit.
  • the first cam element includes a first fork rod having a first cam groove formed on an outer circumferential surface thereof, and the first fork member includes a first cam protrusion moving along the first cam groove to prevent rotation of the first fork rod.
  • the second cam element may be linearly moved along the first fork rod, and the second cam element includes a second fork rod having a second cam groove formed on an outer circumferential surface thereof, and the second fork member moves along the second cam groove. It may be provided to move linearly along the second fork rod corresponding to the rotation of the second fork rod, the first fork rod and the second fork rod may be rotated at the same time by the drive unit.
  • the driving unit may be provided in various structures capable of simultaneously rotating the first cam element and the second cam element.
  • the driving unit may include a power transmission unit for simultaneously transmitting the driving force of the single driving motor and the driving motor to the first cam element and the second cam element.
  • the power transmission unit may be provided in various structures capable of simultaneously transmitting the driving force of the driving motor to the first cam element and the second cam element.
  • the power transmission unit may include a conventional gear combination.
  • the gear combination may be understood to include a combination of single or plural gears.
  • the power transmission unit may be configured to include other power transmission members such as a belt.
  • the power transmission unit is a drive gear coupled to the drive shaft of the drive motor, and And a first gear coupled to the rotation shaft of the one barrel cam member and engaged with the drive gear, and a second gear coupled to the rotation shaft of the second barrel cam member and engaged to the drive gear.
  • first gear and the second gear may rotate in the same rotation direction in response to the rotation of the drive gear, in some cases, the first gear may be rotated in response to the rotation of the drive gear using a separate idle gear. It is also possible to configure the first gear and the second gear to rotate in opposite directions.
  • the power transmission unit is a drive gear coupled to the drive shaft of the drive motor, It may be configured to include a first gear coupled to the first fork rod and engaged with the drive gear, and a second gear coupled to the second fork rod and engaged with the drive gear.
  • a dual clutch transmission device for shifting a synchronizer to realize shifting is connected to a drive unit, a fork rod rotated by the drive unit, and a synchronizer, and to the rotation of the fork rod. And a shift fork correspondingly linearly moving along the fork rod, and as the shift fork moves linearly in response to the rotation of the fork rod, the synchronizer is linearly moved and shifting is realized.
  • Shiftforks may be provided to move synchronizers commonly associated with a particular countershaft.
  • a synchronizer commonly associated with a specific counter shaft may be understood as a synchronizer for shifting driven gears installed in the specific counter shaft.
  • the structure in which the shiftfork moves linearly along the fork rod by the rotation of the fork rod can be variously changed according to the required conditions and design specifications.
  • a cam groove may be formed at one side of the fork rod and the shift fork
  • a cam protrusion accommodated at the cam groove may be formed at the other side of the fork rod and the shift fork, and the cam protrusion may correspond to the rotation of the fork rod.
  • the shift fork can move linearly with respect to the fork rod.
  • the cam groove may be formed in various structures according to the required conditions and design specifications.
  • the cam groove may be formed in a form in which both ends are connected to the outer surface of the fork rod, and the cam protrusion may be circulated along the cam groove and move as the fork rod rotates.
  • the angle and structure of the cam groove may be appropriately changed according to the required conditions and design specifications, and the present invention is not limited or limited by the angle and structure of the cam groove.
  • the cam groove may be formed in a form in which both ends are separated. That is, the cam groove may provide a broken path at both ends thereof.
  • the driving unit may move the interlock pin connected to the shift fork to a desired position while the fork rod is rotated forward or reverse.
  • the cam groove may be formed to have an angle range larger than 360 degrees on the outer surface of the fork rod.
  • the dual clutch transmission is connected to a drive unit, a fork rod rotated by the drive unit, and a synchronizer, and a shift fork linearly moving along the fork rod in response to the rotation of the fork rod.
  • a plurality of fork rods may be provided corresponding to the synchronizer associated with a particular countershaft
  • a plurality of shift fork may be provided corresponding to the plurality of fork rods
  • the drive unit to correspond to a plurality of fork rods
  • a plurality can be provided to drive each of the plurality of fork rods independently.
  • two or three or more fork rods may be used, and the present invention is not limited or limited by the number and arrangement of the fork rods.
  • the plurality of fork rods may be disposed coaxially or non-coaxially with each other, and in some cases, the fork rods may be disposed to be inclined to each other or may be arranged in other structures.
  • the transmission according to the invention can be applied to a single clutch comprising only one counter shaft.
  • the structure can be simplified and shift control is easy.
  • the first shift fork unit and the second shift fork unit are simultaneously driven by only one drive unit, without having to individually provide a driving unit for operating the first shift fork unit and the second shift fork unit. Since it can be operated, the structure can be simplified, and shift control is easier because only one motor needs to be controlled.
  • the present invention since only one driving unit is used, it can contribute to the miniaturization of the device, reduce the cost, and improve the vehicle mountability.
  • 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 easier.
  • FIG. 1 is a view for explaining the configuration of a dual clutch transmission according to the present invention.
  • FIG. 2 is a view showing the structure of a dual clutch transmission according to the present invention.
  • FIG. 3 is a diagram illustrating a cam groove of a barrel cam member as a dual clutch transmission according to the present invention.
  • FIG. 4 is a view showing a modification of the dual clutch transmission according to the present invention.
  • 5 and 6 are views showing the structure of a dual clutch transmission according to another embodiment of the present invention.
  • FIG. 7 is a view for explaining the configuration of a dual clutch transmission according to another embodiment of the present invention.
  • FIG 8 to 10 are views showing the structure of a dual clutch transmission according to another embodiment of the present invention.
  • 11 and 12 are diagrams for explaining the cam groove of the fork rod as a dual clutch transmission according to another embodiment of the present invention.
  • FIG. 13 is a diagram illustrating a dual clutch transmission device 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
  • Figure 2 is a view showing the structure of a dual clutch transmission according to the present invention
  • 3 is a diagram illustrating a cam groove of a barrel cam member as a dual clutch transmission device according to the present invention
  • FIG. 4 is a view showing a modification of the dual clutch transmission device according to the present invention.
  • the dual clutch transmission apparatus includes a gear shift unit and a shift unit.
  • 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 fork members 316a, 316b and the second fork members 326a of the first and second shift fork units 310 and 320 are respectively provided in the first to fourth synchronizers 31, 32, 33, and 34.
  • a fastening groove (not shown) for fastening the 326b may be formed, and the first to fourth synchronizers 31, 32, 33, and 34 may include the first fork members 316a, 316b and the second fork members.
  • 326a and 326b are moved in the axial direction, whereby rotation of the driven gears G1, G2, G3, G4, G5, G6, G7, G8 causes the first counter shaft 23 or the second counter shaft 24 to rotate. To be motivated.
  • the shift unit is provided for shifting the gear shift unit, and includes a first shift fork unit 310, a second shift fork unit 320, and a driving unit 100.
  • 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 first shift fork unit 310 and the second shift fork unit 320 perform a shift operation, the first shift fork unit 310 and the second shift fork unit 320. It can be understood that the shift is performed by operating the driving force of the driving unit 100 and moving the corresponding synchronizer.
  • the first shift fork unit 310 moves in response to the rotation of the first cam element and the first cam element, and moves the synchronizers 33 and 34 adjacent to the first counter shaft 23. It may include a first fork member (316a, 316b) for performing a shift (shift) operation, the second shift fork unit 320 corresponds to the rotation of the second cam element, and the second cam element And the second fork members 326a and 326b to move the synchronizers 31 and 32 adjacent to the second counter shaft 24 to perform a shift operation.
  • first cam element of the first shift fork unit 310 and the second cam element of the second shift fork unit 320 rotational movement may be performed by the first fork members 316a and 316b and the second fork member (
  • Various cam members that can be converted into linear motions of 326a and 326b may be used, and the structures and characteristics of the first cam element and the second cam element may be variously changed according to required conditions and design specifications.
  • the first shift fork unit 310 has a first cam groove 318a is formed along the outer circumferential surface and rotated by the first barrel cam member 318 rotated by the driving unit 100 to be described later, and the synchronizer described above.
  • First fork members 316a and 316b connected to each other and moving along the first cam groove 318a in response to the rotation of the first barrel cam member 318 and linearly moving along the axial direction of the first barrel cam member 318.
  • the second shift fork unit 320 may include a second barrel cam member 328 formed along the outer circumferential surface thereof and rotated by the driving unit 100, and the synchro.
  • a second fork member 326a connected to the niger and moving along the second cam groove 328a in response to the rotation of the second barrel cam member 328 and linearly moving along the axial direction of the second barrel cam member 328. 326b).
  • profiles of the first cam groove 318a and the second cam groove 328a may be appropriately changed according to required conditions and design specifications, and the present invention is limited by the profile of the first cam groove and the second cam groove. It is not limited.
  • the first cam groove 318a and the second cam groove 328a are formed in a form in which both ends thereof are connected to the outer surfaces of the first barrel cam member 318 and the second barrel cam member 328.
  • the first fork members 316a and 316b and the second fork members 326a and 326b may have a first cam groove 318a as the first barrel cam member 318 and the second barrel cam member 328 rotate.
  • the second cam groove 328a may be circulated and moved.
  • both ends of the first cam groove and the second cam groove may be separated.
  • the first cam groove (or the second cam groove) may provide a disconnected path at both ends thereof.
  • the first cam groove may extend the angle range formed at the outer surface of the first barrel cam member to 360 degrees or more, and the first cam groove does not overlap each other.
  • the length of the cam groove can be formed longer.
  • 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 driving unit 100 provides a driving force for driving the first shift fork unit 310 and the second shift fork unit 320, and the first shift fork unit 310 and the second by the driving unit 100.
  • the shift fork unit 320 may be driven at the same time.
  • the driving unit 100 may be provided in various structures capable of simultaneously driving the first shift fork unit 310 and the second shift fork unit 320.
  • the driving unit 100 may include a single driving motor 110 and the power transmission unit 120.
  • the driving motor 110 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 power transmission unit 120 may be provided in various structures capable of simultaneously transmitting the driving force of the driving motor 110 to the first shift fork unit 310 and the second shift fork unit 320.
  • the power transmission unit 120 may include a conventional gear combination.
  • the gear combination may be understood to include a combination of single or plural gears.
  • the power transmission unit may be configured to include other power transmission members such as a belt.
  • the power transmission unit 120 is coupled to the drive shaft 122 coupled to the drive shaft of the drive motor 110, the rotary shaft of the first barrel cam member 318 and engaged with the drive gear 122.
  • An example configured to include a first gear 124 and a second gear 126 coupled to the rotation shaft of the second barrel cam member 328 and engaged with the drive gear 122 will be described.
  • the present invention has been described with an example in which the first gear and the second gear are configured to rotate in the same rotation direction in response to the rotation of the drive gear, but in some cases, separate idle gears are used. Therefore, the first gear and the second gear may be configured to rotate in opposite directions to correspond to the rotation of the drive gear.
  • the drive shaft of the drive motor 110 may be directly connected to the first barrel cam member 318
  • the power transmission unit ( 120 may include a drive gear 122 coupled to the drive shaft of the drive motor 110, and a second gear 126 coupled to the rotation shaft of the second barrel cam member 328 and engaged with the drive gear.
  • FIG. 4 illustrates an example in which the first gear and the second gear are configured to rotate in opposite directions.
  • the first gear may correspond to the rotation of the drive gear using a separate idle gear.
  • the second gear may be configured to rotate in the same direction.
  • the drive shaft of the drive motor may be directly connected to the first barrel cam member, and the power transmission unit may include the drive gear and the first gear.
  • FIG. 5 and 6 are views showing the structure of 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 apparatus includes a first shift fork unit 310 ′, a second shift fork unit 320 ′, and a driving unit 100 ′.
  • the first shift fork unit 310 ′ and the second shift fork unit 320 ′ are connected to the fork rods 314 ′ and 324 ′ and the synchronizer (see FIGS. 31 to 34 in FIG. 1) and the fork rod 314.
  • And fork members 316 ', 316b', 326a ', and 326b' that move linearly along the fork rods 314 'and 324' in response to the rotation of ', 324'.
  • the fork rods 314 'and 324' of the fork units 310 'and 320' may be rotated simultaneously by the driving unit.
  • the first shift fork unit 310 ′ is connected to the first fork rod 314 ′ and the above-described synchronizer (see 33 and 34 in FIG. 1) and the first fork rod 314.
  • the first fork members 316a 'and 316b' linearly move along the first fork rod 314 'in response to the rotation of').
  • a first cam groove 314a ' is formed on an outer circumferential surface of the first fork rod 314', and a first cam groove 314a 'is accommodated in the first fork members 316a' and 316b '.
  • a cam protrusion 317 ' is formed, and the first cam member 317' moves along the first cam groove 314a 'in response to the rotation of the first fork rod 314'.
  • 316a 'and 316b' will be described as an example configured to move linearly with respect to the first fork rod 314 '.
  • 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 structure of the first cam groove 314a' is required. It may be changed according to the conditions and design specifications.
  • the second shift fork unit 320 ′ is connected to the second fork rod 324 ′ and the synchronizer (see FIGS. 31 and 32 in FIG. 1) and corresponds to the rotation of the second fork rod 324 ′.
  • the second fork members 326a 'and 326b' may be linearly moved along the fork rod 324 '.
  • the first shift fork unit 310 ′ and the second shift fork unit 320 ′ are described with the same structure. However, in some cases, the first shift fork unit may be described. And the second shift fork unit may be made of a different structure.
  • a second cam groove 324a ' is formed on an outer circumferential surface of the second fork rod 324', and a second cam groove 324a 'is accommodated in the second fork members 326a' and 326b '.
  • the cam protrusion 327 ' is formed, and the second cam member 327' moves along the second cam groove 324a 'in response to the rotation of the second fork rod 324'.
  • 326a 'and 326b' will be described as an example configured to move linearly with respect to the second fork rod 324 '.
  • 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' is required. It may be changed according to the conditions and design specifications.
  • the driving unit may be provided in various structures capable of simultaneously driving the first fork rod 314 ′ and the second fork rod 324 ′ of the first shift fork unit 310 ′ and the second shift fork unit 320 ′. have.
  • the driving unit may include a single driving motor 110 ′ and a power transmission unit 120 ′, wherein the power transmission unit 120 ′ is coupled to the drive shaft of the driving motor 110 ′.
  • Figure 7 is a view for explaining the configuration of the dual clutch transmission device according to another embodiment of the present invention
  • Figures 8 to 10 are views showing the structure of the dual clutch transmission device according to another embodiment of the present invention. to be.
  • 11 and 12 are diagrams illustrating a cam groove of a fork rod as a dual clutch transmission device according to another embodiment of the present invention
  • FIG. 13 is a dual clutch transmission device according to another embodiment of the present invention. The figure is shown.
  • a dual clutch transmission device includes a gear shift unit and a shift unit.
  • 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 1320, which will 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 1320 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 1310 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 1310 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 shift forks 1316a, 1316b, and second shift forks of the first and second shift forks 1310 and 1320, respectively.
  • Fastening grooves (not shown) for fastening the 1326a and 1326b may be formed, and the first to fourth synchronizers 31, 32, 33, and 34 may include the first shift forks 1316a and 1316b and the second.
  • the shift unit may be provided to shift the shift gear unit, and may include a first shift fork unit 1310 and a second shift fork unit 1320.
  • first shift fork unit 1310 and the second shift fork unit 1320 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 1310 may be provided to move the synchronizers 34 and 33 commonly associated with the first counter shaft 23, and include a first driving motor 1312 and the first driving motor.
  • the first shift forks 1316a and 1316b are provided to move the synchronizers 34 and 33 commonly associated with the first counter shaft 23, and include a first driving motor 1312 and the first driving motor.
  • a first fork rod 1314 that is rotated by 1312, and the synchronizers 34 and 33, and linearly move along the first fork rod 1314 in response to the rotation of the first fork rod 1314.
  • the first shift forks 1316a and 1316b may be provided to move the synchronizers 34 and 33 commonly associated with the first counter shaft 23, and include a first driving motor 1312 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 1312 provides a driving force for rotating the first fork rod 1314, which will be described later.
  • a general motor may be used as the first driving motor 1312, and the present invention is not limited or limited by the type and characteristics of the first driving motor 1312.
  • 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 1316a and 1316b are connected to the synchronizers 34 and 33 associated with the first counter shaft 23, and the first fork rods 1314 correspond to the rotation of the first fork rods 1314.
  • the first shift forks 1316a and 1316b are linearly moved in response to the rotation of the first fork rod 1314, and the synchronizer (1) associated with the first counter shaft 23 34 and 33 are linearly moved and shifting can be implemented.
  • first cam groove 1314a may be formed on an outer circumferential surface of the first fork rod 1314 and a first cam protrusion accommodated in the first cam groove 1314a in the first shift forks 1316a and 1316b.
  • 1317 may be formed, and as the first cam protrusion 1317 moves along the first cam groove 1314a in response to the rotation of the first fork rod 1314, the first shift forks 1316a and 1316b. May linearly move relative to the first fork rod 1314.
  • 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 1314a may be formed in a form in which both ends thereof are connected to the outer surface of the first fork rod 1314, and the first cam protrusion 1317 may have a first fork rod. As the 1313 rotates, the first cam groove 1314a may be circulated and moved.
  • the angle and structure of the first cam groove 1314a 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 1314a. .
  • the second shift fork unit 1320 may be provided to move the synchronizer commonly associated with the second counter shaft 24, and may be provided by the second driving motor 1322 and the second driving motor 1322.
  • Second fork rods 1324 rotating and second shift forks 1326a and 1326b connected to the synchronizer and linearly moving along the second fork rods 1324 in response to the rotation of the second fork rods 1324. 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 1322 provides a driving force for rotating the second fork rod 1324.
  • a general motor may be used as the second driving motor 1322, and the present invention is not limited or limited by the type and characteristics of the second driving motor 1322.
  • 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 1326a and 1326b are connected to a synchronizer associated with the second countershaft 24 and linearly move along the second fork rod 1324 in response to the rotation of the second fork rod 1324. As the second shift forks 1326a and 1326b linearly move in response to the rotation of the second fork rod 1324, the synchronizer associated with the second countershaft 24 is linearly moved and the shift is performed. Can be implemented.
  • the structure in which the second shift forks 1326a and 1326b are linearly moved along the second fork rod 1324 by the rotation of the second fork rod 1324 may be variously changed according to required conditions and design specifications.
  • a second cam groove 1324a may be formed on an outer circumferential surface of the second fork rod 1324 and a second cam protrusion accommodated in the second cam groove 1324a in the second shift forks 1326a and 1326b.
  • 1327 may be formed and second shift forks 1326a and 1326b move as the second cam protrusion 1327 moves along the second cam groove 1324a in response to the rotation of the second fork rod 1324. May linearly move relative to the second fork rod 1324.
  • the second cam groove 1324a may be formed in a form in which both ends thereof are connected to the outer surface of the first fork rod 1314, and the second cam protrusion 1327 may have a second fork rod. As the 1324 rotates, it is circulated along the second cam groove 1324a and may move.
  • the angle and structure of the second cam groove 1324a 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 1324a. .
  • 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 1314a ′′ (or the second cam groove) may provide a broken path at both ends thereof.
  • the first cam groove 1314a ′′ (or the second cam groove) may be 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 1312 (or the second driving motor) is connected to the first shift forks 1316a and 1316b (or the second shift fork) while rotating the first fork rod 1314 forward or reverse.
  • the interlock pin (not shown) may be moved to a desired position.
  • the first cam groove 1314a ′′ (or the second cam groove) may extend the angle range formed at the outer surface of the first fork rod 1314 to 360 degrees or more, instead of being separated at both ends. 1314a "may be longer than the first cam groove 1314a" in the range which does not overlap each other.
  • the 1st cam groove 1314a "of FIG. 12 is the 1st cam groove 1314a shown in FIG.
  • the first cam groove 1314a can be formed in a longer path or a larger angle range in the first fork rod 1314 having the same diameter.
  • the slope of the inclined section for changing the position of the interlock pins connected to the first shift forks 1316a and 1316b in the first cam groove 1314a ′′ may be formed more gently, thereby minimizing interference during shifting. It is also possible to increase the speed of the shift more quickly, that is, the structure of the first cam groove 1314a "(or the second cam groove) of FIG. 12 is possible by the first fork rod 1314 (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 1314, 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 more precise control. It can bring many technical advantages such as lower driving motor cost.
  • FIG. 9 illustrates an example in which the first fork rod 1314 and the second fork rod 1324 have the same diameter or thickness as a whole, but in some cases, as shown in FIG. 10, the first fork rod
  • the portion where the first cam groove 1314a and the second cam groove 1324a are formed in the 1314 and the second fork rod 1324 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 13 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 1314 ′ that is rotated by driving motors 1312 ′ and 1322 ′ and the driving motors 1312 ′ and 1322 ′. 1324 ', and shift forks 1316a' connected to the synchronizers 31 to 34 and linearly moving along the fork rods 1314 'and 1324' in response to rotation of the fork rods 1314 'and 1324'. 1316b ', 1326a' and 1326b ', wherein the fork rods 1314' and 1324 'may be provided in plurality in correspondence with synchronizers 31 to 34 associated with specific countershafts 23 and 24.
  • the shift forks 1316a ', 1316b', 1326a 'and 1326b' may be independently provided to the fork rods 1314 'and 1324', respectively, and the driving motors 1312 'and 1322' may be provided as fork rods ( 1314 'and 1324' are provided in plurality so as to independently drive the fork rods 1314 'and 1324', respectively.
  • first fork rods 1314 ′ constituting the first shift fork unit 1310 ′ may be provided at two intervals at predetermined intervals, and each of the first fork rods 1314 ′ may be provided with a first fork rod 1314 ′.
  • the shift forks 1316a 'and 1316b' may be provided one by one, and each of the first fork rods 1314 'may be independently driven by different first driving motors 1312'.
  • two second fork rods 1324 'constituting the second shift fork unit 1320' may be provided with two spaced apart at predetermined intervals, and each second fork rod 1324 'has a second shift.
  • Forks 1326a 'and 1326b' may be provided one by one, and each of the second fork rods 1324 'may be independently driven by different second driving motors 1322'.
  • first shift forks 1316a ′ and 1316b ′ provided to the first fork rods 1314 ′ may be connected to synchronizers 34 and 33 commonly associated with the first counter shaft 23.
  • the second shift forks 1326a 'and 1326b' provided to each of the second fork rods 1324 ' may be connected to synchronizers 32 and 31 commonly associated with the second counter shaft 24.
  • the plurality of first fork rods 1314 ′ may be coaxially or non-coaxially disposed with each other, and likewise, the plurality of second fork rods 1324 ′ may also be coaxially or non-coaxially disposed with each other.
  • first fork rods 1314 ′ are coaxially arranged with each other and a plurality of second fork rods 1324 ′ 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 1314 ′ and the second fork rod 1324 ′, and corresponding shift forks ( 1316a ', 1316b', 1326a 'and 1326b' may be formed with a cam protrusion (see 317 of FIG. 13) accommodated in the cam groove, and the first fork rod 1314 'and the second fork rod 1324' may be formed.

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

Abstract

L'invention concerne une transmission à double embrayage permettant de simplifier une structure et permettant de changer une vitesse de manière simple. La transmission à double embrayage, permettant de changer la vitesse par le déplacement d'un synchroniseur dans un embrayage double comprenant un premier arbre intermédiaire et un second arbre intermédiaire, comporte : une première unité de fourchette de boîte ayant un premier élément de came, et un premier élément de fourchette déplacé en fonction de la rotation du premier élément de came et mettant en oeuvre une opération d'embrayage par le déplacement du synchroniseur adjacent au premier arbre intermédiaire ; une seconde unité de fourchette de boîte ayant un second élément de came, et une seconde fourchette déplacée en fonction de la rotation du second élément de came et mettant en oeuvre une opération d'embrayage par le déplacement du synchroniseur adjacent au second arbre intermédiaire ; et une unité d'entraînement permettant la rotation simultanée du premier élément de came et du second élément de came.
PCT/KR2014/000635 2013-01-23 2014-01-22 Transmission à double embrayage Ceased WO2014116028A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR1020130007408A KR101420700B1 (ko) 2013-01-23 2013-01-23 듀얼클러치 변속장치
KR10-2013-0007413 2013-01-23
KR1020130007413A KR101390339B1 (ko) 2013-01-23 2013-01-23 듀얼클러치 변속장치
KR10-2013-0007408 2013-01-23

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WO2014116028A1 true WO2014116028A1 (fr) 2014-07-31

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Application Number Title Priority Date Filing Date
PCT/KR2014/000635 Ceased WO2014116028A1 (fr) 2013-01-23 2014-01-22 Transmission à double embrayage

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WO (1) WO2014116028A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101795734B1 (ko) 2016-05-20 2017-12-01 한국파워트레인 주식회사 듀얼 클러치 변속기의 구동장치
WO2024256384A1 (fr) * 2023-06-16 2024-12-19 Pinion Gmbh Dispositif de changement de vitesse pour une transmission de bicyclette, unité de transmission et procédé de changement de vitesse

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6799484B2 (en) * 2001-07-25 2004-10-05 Zf Friedrichshafen Ag Actuator device for a servo-shifted transmission of a vehicle
US20090193918A1 (en) * 2008-01-31 2009-08-06 Yoshiaki Tsukada Twin clutch transmission
US20110100144A1 (en) * 2009-11-04 2011-05-05 Gm Global Technology Operations, Inc. Barrel cam shift mechanism
KR101034890B1 (ko) * 2010-05-13 2011-05-17 주식회사 로보멕 듀얼 클러치 변속기의 시프트장치
EP2322371A1 (fr) * 2009-11-13 2011-05-18 C.R.F. Società Consortile per Azioni Système de propulsion hybride de véhicule à moteur incluant une transmission à double embrayage avec un dispositif de levier de vitesses comportant un tambour rotatif

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6799484B2 (en) * 2001-07-25 2004-10-05 Zf Friedrichshafen Ag Actuator device for a servo-shifted transmission of a vehicle
US20090193918A1 (en) * 2008-01-31 2009-08-06 Yoshiaki Tsukada Twin clutch transmission
US20110100144A1 (en) * 2009-11-04 2011-05-05 Gm Global Technology Operations, Inc. Barrel cam shift mechanism
EP2322371A1 (fr) * 2009-11-13 2011-05-18 C.R.F. Società Consortile per Azioni Système de propulsion hybride de véhicule à moteur incluant une transmission à double embrayage avec un dispositif de levier de vitesses comportant un tambour rotatif
KR101034890B1 (ko) * 2010-05-13 2011-05-17 주식회사 로보멕 듀얼 클러치 변속기의 시프트장치

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101795734B1 (ko) 2016-05-20 2017-12-01 한국파워트레인 주식회사 듀얼 클러치 변속기의 구동장치
WO2024256384A1 (fr) * 2023-06-16 2024-12-19 Pinion Gmbh Dispositif de changement de vitesse pour une transmission de bicyclette, unité de transmission et procédé de changement de vitesse

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