KR20140144836A - Shifting apparatus for clutch transmission - Google Patents

Shifting apparatus for clutch transmission Download PDF

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Publication number
KR20140144836A
KR20140144836A KR1020130066900A KR20130066900A KR20140144836A KR 20140144836 A KR20140144836 A KR 20140144836A KR 1020130066900 A KR1020130066900 A KR 1020130066900A KR 20130066900 A KR20130066900 A KR 20130066900A KR 20140144836 A KR20140144836 A KR 20140144836A
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KR
South Korea
Prior art keywords
groove
barrel cam
cam member
shift fork
barrel
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KR1020130066900A
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Korean (ko)
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KR101537785B1 (en
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강구태
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넥스테크 (주)
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Publication of KR20140144836A publication Critical patent/KR20140144836A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/14—Control of torque converter lock-up clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • 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
    • 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

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

Abstract

Disclosed is a clutch transmission device capable of simplifying a structure and simply implementing a shift. A clutch shifting device for shifting a synchronizer to move a synchronizer includes a barrel cam member having a cam groove formed therein and a shift fork that moves along the cam groove and linearly moves the synchronizer in response to rotation of the barrel cam member, The cam groove includes a first balance groove, an inclined groove continuously connected to the first balance groove, and a second balance groove continuously connected to the inclined groove, wherein the inclined groove has a different movement path And the shift fork moves in different travel paths in the inclined grooves along the rotational direction of the barrel cam member.

Description

[0001] SHIFTING APPARATUS FOR CLUTCH TRANSMISSION [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a clutch transmission, and more particularly, to a clutch transmission capable of reducing a shift shock and realizing a high shift speed.

Generally, the clutch is used to temporarily cut off or engage the engine. Among them, the dual clutch transmission is provided with two clutches unlike the conventional single-plate clutch transmission system, and one clutch forms a separate transmission system that allows the even-numbered gear and the other clutch to interlock the even-numbered gear , Which is widely used because of its ease of operation, low power loss, and fast shift time.

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

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

In this connection, a "shift device of a dual clutch transmission" is disclosed in Japanese Patent Registration No. 10-1034890. The shift device includes a first input shaft and a second input shaft which are connected to the first clutch and the second clutch, respectively. The two input shafts are suitably provided with drive gears for the first to seventh gears, A counter shaft and a second counter shaft are provided with driven gears engaging the drive gears. Approximately four synchronizers are provided between driven gears and one barrel cam is provided adjacent to the fork rod to operate four shift forks for four synchronizers. The shift fork includes a follow pin, which can position the shift fork to the right, left, or intermediate position as the follow pin moves along the cam groove of the barrel cam.

Meanwhile, the cam groove formed in the barrel cam for actuating the shift fork may be constituted by continuously connecting the plurality of inclined grooves and the equal grooves so as to have a predetermined rule. However, conventionally, since the inclined grooves of the cam grooves are formed so as to provide uniform movement paths irrespective of the rotational direction of the barrel cam member, there is a problem that it is difficult to simultaneously realize the quick shifting and minimizing the shift shock.

That is, generally, the cam groove of the barrel cam may include a first flat groove, an inclined groove connected to the first flat groove, and a second flat groove connected to the inclined groove, The shift pins connected to the fork can be shifted to different shift states (different shift stages or neutral states) as they move to the first balance groove or the second balance groove through the inclined grooves. Further, when the follow-up pin disposed in the first balancing groove moves upward along the inclined groove corresponding to the first directional rotation (e.g., clockwise rotation) of the barrel cam, as the gradient of the inclined groove decreases, The impact can be reduced. On the other hand, when the follow-up pin arranged in the second balance groove moves downward along the inclined groove corresponding to the second direction rotation (for example, counterclockwise rotation) of the barrel cam, The larger the gradient of the inclined groove, the shorter the shift time.

However, conventionally, when the follow-up pin disposed in the first balance groove corresponding to the rotation of the barrel cam in the first direction is moved upward along the inclined groove, and when the barrel cam is rotated in the second direction, Both the downward movement of the follower pin and the downward movement of the follower groove move the same along the inclined groove.

Accordingly, in recent years, various studies have been made on a clutch transmission for simultaneously realizing a quick shifting and minimizing a shift shock, but there is still insufficient development of the clutch shifting device.

The present invention provides a clutch transmission device capable of reducing a shift shock and realizing a quick shift.

Further, the present invention provides a clutch transmission device that can simplify the structure and can easily control the shift.

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

According to a preferred embodiment of the present invention for achieving the above-mentioned objects of the present invention, a clutch transmission device for shifting a synchronizer to realize a shift is provided with a barrel cam member having a cam groove formed therein, The cam groove includes a first flat groove, an inclined groove continuously connected to the first flat groove, a second flat groove continuously connected to the inclined groove, And the inclined grooves provide different movement paths in accordance with the rotational direction of the barrel cam member, and the shift forks move in different travel paths in the inclined grooves along the rotational direction of the barrel cam member.

The shift fork can be provided with a follow pin accommodated in the cam groove. As the follow pin moves along the cam groove corresponding to the rotation of the barrel cam member, the shift fork can linearly move left and right on the fork rod. The synchronizer can be moved linearly.

The cam grooves can be provided in various structures capable of providing different movement paths in accordance with the rotational direction of the barrel cam member. For example, the cam grooves may be formed in such a manner that both ends of the cam groove are continuous from the outer surface of the barrel cam member. In some cases, both ends of the cam groove may be formed in a separated form. Further, in the case where both ends of the cam groove are separated, the cam groove may be formed to have an angular range larger than 360 degrees on the outer surface of the barrel cam member.

For reference, in the present invention, the shift fork is moved in different travel paths in the inclined grooves along the rotational direction of the barrel cam member. For example, when the barrel cam member is rotated in the first direction (for example, And the shift path of the shift fork moving along the cam groove corresponding to the rotation of the barrel cam member in the second direction (for example, counterclockwise rotation) is different from that of the shift fork ≪ / RTI >

The cam groove may include a first balance groove, an inclined groove, and a second balance groove, wherein the inclined grooves may be provided in various structures capable of providing different travel paths in accordance with the rotational direction of the barrel cam member. For example, the inclined grooves may include a first inclined wall having one end connected to the first equilibrium groove and the other end connected to the second equilibrium groove, and a second inclined wall having a different grade from the first inclined wall, And a second inclined wall having one end connected to the first equilibrium groove and the other end connected to the second equilibrium groove, wherein the shift fork comprises a first inclined portion having a different gradient along the rotational direction of the barrel cam member, It can move along the wall or the second inclined wall. For reference, the angles of the first inclined wall and the second inclined wall may be appropriately changed in accordance with required conditions and design specifications, and the number and arrangement interval of the inclined grooves may be variously changed according to required conditions and design specifications have. More specifically, the first shift fork may be provided to move upward along the first inclined wall corresponding to the first directional rotation of the first barrel cam member, 1 shift fork is provided to move downward along the second inclined wall, and the second inclined wall may be formed to have a relatively larger gradient than the first inclined wall.

For reference, the clutch may be configured to include a first counter shaft and a second counter shaft provided to be spaced apart from each other, and the barrel cam member may be configured to actuate a first shift fork mounted on a first fork rod adjacent to the first counter shaft And a second barrel cam member for actuating a second shift fork mounted on a second fork rod adjacent to the second counter shaft. In some cases, it is also possible that the clutch is composed of a single counter shaft and a single barrel cam member.

According to the clutch transmission according to the present invention, the shift shock can be reduced and the shift speed can be increased.

Particularly, according to the present invention, the inclined grooves formed on the barrel cam member can provide different movement paths in accordance with the rotational direction of the barrel cam member, so that different shift characteristics can be realized through one cam groove. Therefore, the shift control is easier and the optimum shift design can be achieved in each shift section.

In addition, according to the present invention, it is possible to realize different shift characteristics through one cam groove without forming several cam grooves having different characteristics in order to implement different shift characteristics, so that the structure can be simplified.

Further, according to the present invention, the space and weight occupied by the barrel cam member can be reduced to realize a compact design and a quick reaction speed, and a simple structure, easy shift control, cost reduction can be achieved, .

1 is a view for explaining a configuration of a clutch transmission according to the present invention.
Figs. 2 to 4 are views for explaining the structure and operating structure of the cam groove, which is the clutch transmission according to the present invention. Fig.
4 is a view for explaining another example of the cam groove, which is the clutch transmission according to the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Reference will now be made in detail to the preferred embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the like elements throughout. For reference, the same numbers in this description refer to substantially the same elements and can be described with reference to the contents described in the other drawings under the above-mentioned rules, and the contents which are judged to be obvious to the person skilled in the art or repeated can be omitted.

FIG. 1 is a view for explaining a configuration of a clutch transmission according to the present invention, and FIGS. 2 to 4 are views for explaining a structure and an operating structure of a cam groove as a clutch transmission device according to the present invention, Fig. 8 is a view for explaining another example of the cam groove as the clutch transmission according to the present invention. Fig.

1 to 4, a clutch transmission according to the present invention includes a transmission portion and a shift portion.

For example, the transmission unit may include a dual clutch 13 including a first clutch 11 and a second clutch 12, a first input shaft 21 of the first and second clutches 11 and 12, A plurality of driving gears D1 to D8 connected to the input shaft 22 and a plurality of driven gears G1 to G8 provided respectively to the first counter shaft 23 and the second counter shaft 24, .

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

As the dual clutch including the first clutch 11 and the second clutch 12, a conventional dual clutch may be used, and the present invention is not limited or limited by the type and characteristics of the dual clutch. For example, the first clutch 11 and the second clutch 12 may be configured to transmit the rotational force of the engine to the first input shaft 21 or the second input shaft 22 through normal hydraulic control. For reference, in the present invention, an example in which the dual clutch is applied to the clutch transmission is described, but in some cases, a single clutch may be applied.

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

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

The plurality of 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, a gear ratio. More specifically, the Hall device driving gears D1, D3, D5 and D7 of the plurality of driving gears D1 to D8 may be connected to the first input shaft 21 and the even numbered driving gears D2, D4, D6 and D8 May be connected to the second input shaft 22.

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

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

For example, the first synchronizer 31 is provided so as to be spline-coupled to the second counter shaft 24 so as to be positioned between the sixth driven gear G6 and the second driven gear G2, Can be shifted by the second shift fork unit 420 to be described later to be engaged with the gear G6 or the second driven gear G2. The second synchronizer 32 is disposed on one side of the first synchronizer 31 and spline coupled to the second counter shaft 24 so as to be positioned between the fifth driven gear G5 and the first driven gear G1. And can be shifted by the second shift fork unit 420 so as to be coupled to the fifth driven gear G5 or the first driven gear G1. The third synchronizer 33 is arranged to face the first synchronizer 31 and is disposed on the first counter shaft 23 so as to be positioned between the eighth driven gear G8 and the fourth driven gear G4 And can be shifted by the first shift fork unit 410 to be described later so as to be splined and coupled to the eighth driven gear G8 or the fourth driven gear G4. The fourth synchronizer 34 is disposed on one side of the third synchronizer 33 and spline coupled to the first counter shaft 23 so as to be positioned between the seventh driven gear G7 and the third driven gear G3. And can be shifted by the first shift fork unit 410 to be described later so as to be engaged with the seventh driven gear G7 or the third driven gear G3.

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

The first to fourth synchronizers 31, 32, 33 and 34 are connected to the first shift forks 316a and 316b and the second shift forks 326a and 326b of the first and second shift fork units 410 and 420, respectively. The first to fourth synchronizers 31, 32, 33, and 34 may be provided with first and second shift forks 316a and 316b and second and third shift forks 316a and 316b, The rotation of the driven gears G1, G2, G3, G4, G5, G6, G7 and G8 is transmitted to the first counter shaft 23 and the second counter shaft 24 by being moved in the axial direction by the first and second countershafts 326a, Lt; / RTI >

The shift portion is provided for shifting the transmission gear portion and includes a first shift fork unit 410 and a second shift fork unit 420. [

The first shift fork unit 410 is configured to be able to perform a shift operation by moving the synchronizers 33 and 34 adjacent to the first counter shaft 23, 2 synchronizer 31 and 32 adjacent to the counter shaft 24 so as to perform a shift operation.

The first shift fork unit 410 includes a first barrel cam member 314 provided to actuate first shift forks 316a and 316b mounted on a first fork rod 314 adjacent to the first counter shaft 23, And a first driving unit 412 for driving the first and second barrel cam members 414a and 414b and the first barrel cam members 414a and 414b.

For example, the first fork rod 314 is provided adjacent to the first counter shaft 23, and on the first fork rod 314, two first forks 316a and 316b are slidably movable Can be provided. One of the two first shift forks 316a and 316b is provided between the driven gears G3 and G7 for the third and seventh stages and the other one of the two first shift forks 316a and 316b And the driven gears 316b are provided between the driven gears G4 and G8 for the fourth and eighth stages.

A first cam groove 415 is formed on an outer circumferential surface of the first barrel cam members 414a and 414b and a first cam groove 415 is formed in each of the first shift forks 316a and 316b, Pins 317a and 317b are provided. As the first follow pins 317a and 317b move along the first cam groove 415 in correspondence with the rotation of the first barrel cam members 414a and 414b, the first shift forks 316a and 316b are moved in the X- And the synchronizers 33 and 34 can be linearly moved by the linear movement of the first shift forks 316a and 316b. For reference, in the embodiment of the present invention, a plurality of first barrel cam members 414a and 414b are provided apart from each other, and one first cam groove 415 is formed in each of the first barrel cam members 414a and 414b However, in some cases, it is also possible to form a plurality of first cam grooves on a single barrel cam member.

For example, the first cam groove 415 may be formed in an erratic shape at both ends. The first cam groove 415 may include a first ball groove 416, an inclined groove 417, and a second ball groove 417 414b and by providing different travel paths in accordance with the rotational direction of the first barrel cam members 414a, 414b, the first shift fork can move in the rotational direction of the first barrel cam members 414a, 414b The slant grooves 417 can move in different directions.

For reference, in the present invention, the first shift fork is moved in different travel paths in the inclined grooves 417 along the rotational direction of the first barrel cam members 414a and 414b. For example, The movement path of the first shift fork that moves along the first cam groove 415 corresponding to the first direction rotation (e.g., clockwise rotation) of the members 414a and 414b and the movement route of the first barrel cam members 414a, The movement path of the first shift fork moving along the first cam groove 415 corresponding to the second direction rotation (e.g., counterclockwise rotation) of the first shift fork 414b may be understood to be different.

The inclined grooves 417 of the first cam groove 415 may be provided in various structures capable of providing different movement paths in accordance with the rotational direction of the first barrel cam members 414a and 414b. For example, the inclined grooves 417 may include a first inclined wall 417a having one end connected to the first equilibrium groove 416 and the other end connected to the second equilibrium groove 418, and a first inclined wall 417a connected to the second inclined wall 417a The second inclined wall 418 is connected to the first equilibrium groove 416 and the other end is connected to the second equilibrium groove 418 so as to have a different grade from the first inclined wall 417a. The first shift fork may include a first inclined wall 417a or a second inclined wall 417b having different gradients depending on the rotational direction of the first barrel cam members 414a and 414b, ). ≪ / RTI > The angles? 1 and? 2 of the first inclined wall 417a and the second inclined wall 417b may be appropriately changed in accordance with required conditions and design specifications, and the number and arrangement of the inclined grooves 417 The spacing can vary widely depending on the required conditions and design specifications.

A first shift fork is provided to move upward along the first inclined wall 417a corresponding to the first directional rotation of the first barrel cam members 414a and 414b and the first barrel cam members 414a, The first inclined wall 417b is provided so as to move downward along the second inclined wall 417b in correspondence with the second inclination of the first inclined wall 414b in the second direction, An example formed so as to have a gradient ([theta] 2 > [theta] 1) will be described. 3, the first inclined wall 417a has a relatively gentle inclination .theta.1 so that the first follow pins 317a and 317b received in the first cam grooves 415 are inclined with respect to the first inclined walls 417a , The transmission shock can be minimized by minimizing interference during shifting. 4, since the second inclined wall 417b has a relatively sharp inclination? 2, when the first follow pins 317a and 317b move along the second inclined wall 417b, The shift time can be further shortened.

The first driving unit 412 provides a driving force for driving the first barrel cam members 414a and 414b. The first driving unit 412 may provide driving force to the first barrel cam members 414a and 414b in various ways according to required conditions and design specifications. For example, a conventional driving motor may be used as the first driving unit 412, and the present invention is not limited or limited by the type and characteristics of the motor. It is also possible in some cases to use other driving means instead of the motor.

The first barrel cam members 414a and 414b may be commonly connected to the drive shaft 412a of the single first drive unit (e.g., a drive motor) and simultaneously driven. However, the first barrel cam members 414a and 414b may include other power transmission members It is also possible to transmit the driving force of the first driving unit to the first barrel cam member by using the first barrel cam member, or alternatively, the first barrel cam member may be driven by another separate driving unit.

The second shift fork unit 420 includes a second barrel cam member 322 provided to actuate second shift forks 326a and 326b mounted on a second fork rod 324 adjacent to the second counter shaft 24, 424a and 424b, and a second driving unit 422 for driving the second barrel cam members 424a and 424b.

For example, the second fork rod 324 is provided adjacent to the second counter shaft 24, and on the second fork rod 324, two second shift forks 326a and 326b are slidably movable Can be provided. One of the two second shift forks 326a and 326b is provided between the driven gears G1 and G5 for the first and fifth stages and the other one of the two second shift forks 326a and 326b And the second gear 326b is provided between the driven gears G2 and G6 for the second and sixth gear stages.

A second cam groove 425 is formed on the outer circumferential surface of the second barrel cam members 424a and 424b and a second cam groove 425 is formed in each of the second shift forks 326a and 326b. Pins 327a and 327b are provided. As the second follow pins 327a and 327b move along the second cam groove 425 in correspondence to the rotation of the second barrel cam members 424a and 424b, the second shift forks 326a and 326b are moved in the second direction Can be linearly moved left and right on the rod 324.

The second cam groove 425 may include an inclined groove (not shown) having a first inclined wall and a second inclined wall having different gradients similar to the first cam groove 415 described above, And in some cases, inclined grooves having first inclined walls and second inclined walls having the same gradient.

The second driving portion 422 provides a driving force for driving the second barrel cam members 424a and 424b. The second driving unit 422 can provide driving force to the second barrel cam members 424a and 424b in various ways according to the required conditions and design specifications. For example, the second driving unit 422 may be a conventional driving motor, and the present invention is not limited or limited by the type and characteristics of the motor.

The plurality of second barrel cam members 424a and 424b may be commonly connected to the driving shaft 422a of the single second driving unit (e.g., driving motor) and simultaneously driven. In some cases, the driving force of the second driving unit may be transmitted to the second barrel cam member using another power transmitting member.

In the above-described embodiment of the present invention, both end portions of the first cam groove 415 and the second cam groove 425 are formed to be continuous. However, in some cases, both ends of the first cam groove and the second cam groove May be formed in a separated form.

Referring to FIG. 5, the first cam groove 415 'and the second cam groove 425' may provide a disconnected path at both ends. 2), the first and second barrel cam members 414a and 414b and the second barrel cam members 424a and 424b are rotated forward (see FIG. 2) The first and second follow pins 317a and 317b and the second follow pins 327a and 327b can be moved to a desired movement path.

The first cam groove 415 'and the second cam groove 425' are formed on the outer surfaces of the first and second barrel cam members 414a and 414b and the second barrel cam members 424a and 424b, The angular range can be extended to 360 degrees or more and the length of the first cam groove 415 'can be made longer within a range in which the first cam grooves 415' (or the second cam grooves) do not overlap with each other. For example, the first cam groove 415 'in FIG. 5 may be longer than the first cam groove 415 shown in FIG. 2 in the first barrel cam member 414a, 414b of the same diameter, It is possible to form the first cam groove 415 '. Therefore, even if the first barrel cam members 414a and 414b have a relatively small diameter, a sufficient cam path can be ensured, so that the diameters of the first barrel cam members 414a and 414b can be further reduced, Contributing to miniaturization and weight reduction of the first and second motor drive units 414a and 414b, as well as providing many technical advantages such as quick rotation and accurate control, reduction of driving motor cost, and the like.

Although the first and second barrel cam members 414a and 414b and the second barrel cam member are configured to have the same diameter or thickness in the above-described embodiments of the present invention, The first barrel cam members 414a and 414b and the second barrel cam member may have different diameters or thicknesses and the first barrel cam members 414a and 414b and the first barrel cam members 415 and 414b may be configured to have different diameters or thickness. It is also possible that the portion where the two cam grooves are formed has a relatively large diameter or a large thickness as compared with other portions.

In the embodiment of the present invention, a plurality of first barrel cam members 414a and 414b (or second barrel cam members) are arranged coaxially with each other. However, in some cases, The barrel cam members 414a and 414b (or the second barrel cam members) may be disposed non-concentrically with respect to each other, or alternatively, three or more barrel cam members may be used, It is possible.

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

410: first shift fork unit 414a, 414b: first barrel cam member
415: first cam groove 416: first flat groove
417: Inclined groove 418: Second equilibrium groove
420: second shift fork unit 424a, 424b: second barrel cam member

Claims (8)

1. A clutch transmission device for shifting a synchronizer,
A barrel cam member having a cam groove formed therein; And
And a shift fork that moves along the cam groove and linearly moves the synchronizer in response to rotation of the barrel cam member,
Wherein the cam groove includes: a first flat groove; An inclined groove continuously connected to the first balance groove; And a second balance groove continuously connected to the inclined groove,
Wherein the inclined grooves provide different movement paths in accordance with the rotational direction of the barrel cam member and the shift fork moves in different travel paths in the inclined grooves along the rotational direction of the barrel cam member. Transmission. The method according to claim 1,
The inclined groove
A first inclined wall having one end connected to the first equilibrium groove and the other end connected to the second equilibrium groove; And
A second inclined wall formed to have a different grade from the first inclined wall and having one end connected to the first equalized groove and the other end connected to the second equalized groove so as to be spaced apart from the first inclined wall; Including,
And the shift fork is moved along the first slant wall or the second slant wall in accordance with the rotational direction of the barrel cam member. 3. The method of claim 2,
The shift fork is provided to move upward along the first inclined wall in correspondence with the rotation of the barrel cam member in the first direction,
The shift fork is provided to move downward along the second inclined wall in correspondence with the rotation of the barrel cam member in the second direction,
And the second inclined wall is formed to have a gradient relatively larger than that of the first inclined wall. The method according to claim 1,
And the cam groove is formed so that both ends of the cam groove extend from the outer surface of the barrel cam member. The method according to claim 1,
And the cam groove is formed with both ends separated from the outer surface of the barrel cam member. 6. The method of claim 5,
And the cam groove is formed on an outer surface of the barrel cam member so as to have an angular range larger than 360 degrees. The method according to claim 1,
And a follow pin connected to the shift fork and movably disposed along the cam groove,
And the shift fork is linearly moved as the follow pin moves along the cam groove corresponding to the rotation of the barrel cam member. The method according to claim 1,
The clutch includes a first counter shaft and a second counter shaft provided to be spaced apart from each other,
The barrel cam member includes a first barrel cam member for actuating a first shift fork mounted on a first fork rod adjacent to the first counter shaft and a second barrel cam member for actuating a second shift fork mounted on a second fork rod adjacent to the second counter shaft And a second barrel cam member for actuating the second shift fork.
KR1020130066900A 2013-06-12 2013-06-12 Shifting apparatus for clutch transmission KR101537785B1 (en)

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Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62177339A (en) * 1986-01-27 1987-08-04 Yamaha Motor Co Ltd Shift drum structure of speed change gear
JP2007285363A (en) * 2006-04-13 2007-11-01 Aisin Ai Co Ltd Shift device of gear type automatic transmission
JP4897534B2 (en) * 2007-03-28 2012-03-14 本田技研工業株式会社 Vehicle transmission

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