JP5051398B2 - Transmission - Google Patents

Description

  The present invention relates to a mechanical transmission, and more particularly to the structure of a transmission unit.

  2. Description of the Related Art A mechanical automatic transmission that does not use a torque converter is known as a vehicle transmission. In this mechanical automatic transmission, an automatic transmission that does not require a torque converter is made possible by operating a transmission operation (selection and shift) and a clutch connection / disconnection in a manual transmission with an actuator. The transmission includes, for example, a shaft that can be moved by sliding or rotating in the select direction and the shift direction, a plurality of shift lugs (shift brackets) arranged in the select direction, and shift rails that respectively connect the shift lugs and the shift forks. Rod). Further, the shaft is provided with an arm portion (shifter) protruding outward, and each shift lug is provided with a claw portion. In the mechanical automatic transmission, the actuator is moved in the select direction and the shift direction by the actuator, and the shift lugs are selectively pushed by the arm portion and moved in the shift direction to selectively shift the shift fork. Operate (Patent Document 1).

JP 2001-304411 A

  However, in Patent Document 1 described above, the shift lugs are arranged at intervals in the select direction according to the position of the shift fork. Therefore, it takes time to move the arm portion in the select direction from the claw portion of one shift lug to the claw portion of another shift lug, which is one of the factors for increasing the shift time. In particular, when used in a dual clutch type automatic transmission, the operation of the arm is complicated at the time of shifting, which increases the movement time in the select direction, which is a major factor that hinders shortening of the shifting time. Yes.

Further, when the movement distance of the arm portion in the select direction is relatively large due to the distance in the select direction of the shift lug as described above, an error in the stop position of the arm portion becomes large. In the structure that moves in the select direction, the inertia is large, and it may be difficult to accurately stop at the select position of the desired claw portion.
The present invention has been made to solve such problems, and an object of the present invention is to provide a mechanical transmission that shortens the select operation time and enables a quick shift. is there.

  In order to achieve the above object, the invention of claim 1 includes a shift shaft provided with an arm portion projecting radially outward, an axis extending in the select direction, and a pressing portion pressed by the arm portion. A plurality of shift lugs arranged in the select direction and a shift fork that is connected to the shift lugs via the shift rail and performs a shift operation of the shift speed, and the arm portion shifts the pressing portion perpendicular to the select direction. In a transmission that moves the shift lug in the shift direction by pushing in the direction, and shifts the shift fork via the shift rail, the shift fork is inserted into the shift shaft so as to be movable and rotatable in the select direction, and engagement teeth are formed. The shift shaft is provided with a plurality of cylindrical members arranged coaxially, and a plurality of cylinders are provided. The member is formed with an arm portion at one end portion and an engaging portion that engages with an engaging tooth of the select shift gear at the other end portion, and the select shift gear moves in the select direction. A predetermined cylindrical member is selected, rotated and engaged with the engaging portion of the cylindrical member to selectively rotate the cylindrical member, and the arm portion provided on the cylindrical member is shifted in the shift direction. It is characterized by moving and shifting.

  According to a second aspect of the present invention, in the first aspect, the plurality of engaging portions of the respective cylindrical members or the engaging teeth of the select shift gear are formed in the circumferential direction, and the plurality of engaging portions or the plurality of engaging teeth are formed. The pitch angle of the engagement teeth is determined by the movement of the select shift gear, which has been driven to rotate the shift lug by rotating the predetermined cylindrical member, while moving in the select direction while maintaining the rotation angle. It is set according to the shift stroke of a shift lug so that an engagement tooth may engage with a joint part.

According to a third aspect of the present invention, in the second aspect, the engaging portion of the cylindrical member or the engaging teeth of the select shift gear is formed over the entire circumference in the circumferential direction.
According to a fourth aspect of the present invention, in any one of the first to third aspects, the other end portion of the tubular member extends radially outward to form a flange portion, and an engagement portion is formed at the tip of the flange portion. It is formed.

  According to the transmission of the first aspect of the present invention, the select shift gear is moved in the select direction to be engaged with the engagement portion of the predetermined cylindrical member, and the select shift gear is rotated to rotate the cylindrical member. By selectively rotationally driving, the corresponding shift lug can be shifted by the arm portion provided on the cylindrical member. Particularly, since the shift shaft is configured by coaxially arranging a plurality of cylindrical members, the other end portions of the cylindrical members can be arranged close to each other in the select direction. Therefore, it is possible to reduce the time for the select shift gear to move in the select direction during a shift, and thus it is possible to make a quick shift.

Further, by moving the select shift gear in the select direction at the time of shifting, it is not necessary to move the entire shift shaft in the select direction at the time of selection, and inertia is reduced, so that the stop accuracy of the select position can be improved.
According to the transmission of the second aspect of the present invention, when the shift gear is moved in the select direction from the cylindrical member that has been shifted to another cylindrical member, the engaging teeth and the engaging portion It is possible to engage with other tubular members without having to adjust the rotation angle of the select shift gear so as to be locked. Therefore, the operation of the select shift gear at the time of shifting can be simplified and shifting can be made quicker.

According to the transmission of the third aspect of the present invention, the engaging portion of the cylindrical member or the engaging tooth of the select shift gear is formed over the entire circumference. Even if the range of the rotation angle that can be locked to the portion increases and the shift stroke of the shift lug is set large, it is possible to cope with it.
According to the transmission of the fourth aspect of the present invention, the engaging portions of the cylindrical member can be arranged so as to be arranged in the select direction with a simple configuration.

It is a schematic diagram of a dual clutch type automatic transmission having six forward speeds and one reverse speed to which the present invention is applied. It is a whole block diagram of the operating mechanism of a shift fork. It is a detailed block diagram which shows the shape of the gear for selection shifts, and its connection state. It is a reference figure explaining the pitch angle of the spline groove of a cylindrical member. It is a reference figure explaining the pitch angle of the spline groove | channel of the cylindrical member using a bifurcated arm part.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
FIG. 1 is a schematic diagram of a transmission unit 1 of a dual clutch transmission having six forward speeds and one reverse speed to which the present invention is applied.
As shown in FIG. 1, the transmission unit 1 includes two clutches 2 and 3, two main shafts 4 and 5 disposed coaxially, and two countershafts 6 and 7. . Power is transmitted from the output shaft 9 of the engine 8 to the first main shaft 4 through the first clutch 2, while power is transmitted from the output shaft 9 to the second main shaft 5 through the second clutch 3. It is configured to be.

  The first countershaft 6 and the second countershaft 7 are disposed so as to be spaced apart from each other so that the axes thereof are parallel to the first main shaft 4 and the second main shaft 5, and the rear stage of the transmission unit 1. The differential 10 is configured to be able to transmit power. A first speed gear 11, a second speed gear 12, a third speed gear 13, and a sixth speed gear 14 are rotatably supported on the first countershaft 6. A fourth gear 15, a fifth gear 16, and a reverse gear 17 are pivotally supported on the second countershaft 7 and a parking gear 18 is fixed thereto.

  Further, the transmission unit 1 is provided with four shift forks 20 to 23. The first shift fork 20 and the second shift fork 21 are slidably installed along the axis of the first countershaft 6, and the third shift fork 22 and the fourth shift fork 23 are It is installed so as to be slidable along the axis of the second auxiliary shaft 7. By sliding the shift forks 20 to 23, the second gear 12 and the sixth gear 14 are moved by the first shift fork 20, the first gear 11 and the third gear 13 are moved by the second shift fork 21, Each can selectively connect and disconnect (shift operation) to the countershaft 6, the fourth shift gear 15 and the reverse gear 17 are provided by the third shift fork 22, and the fifth speed gear 16 is provided by the fourth shift fork 23. , Each can be selectively connected to the auxiliary shaft 7 (shift operation). The first main shaft 4 is connected to a first speed gear 11, a third speed gear 13, and a fifth speed gear 16, while the second main shaft 5 is connected to a second speed gear 12, a fourth speed gear 15, a sixth speed gear 14, and A reverse gear 17 is connected.

That is, in the transmission section 1 of the dual clutch transmission, the first clutch 2 can be selectively switched to the first speed, the third speed, and the fifth speed, while the second clutch 3 is used for the second speed. It is configured to be selectively switchable between the 4th speed, 6th speed and reverse.
FIG. 2 is an overall configuration diagram of an operating mechanism of the shift forks 20 to 23. FIG. 3 is a detailed configuration diagram showing the shape of the select shift gear and its connection state.

  As shown in FIG. 2, the shift forks 20 to 23 are fixed to four shift rails 30 a to 30 d that are movably arranged in the front-rear direction (shift direction) in the figure, and further to the shift rails 30 a to 30 d. Are provided with shift lugs 40a to 40d, respectively. The shift lugs 40a to 40d are plate members extending rightward from the shift rails 30a to 30d, and a pair of pressing portions 41a to 41d formed in a claw shape protruding rightward is provided on the right end portion. Each shift lug 40a-40d is arrange | positioned at intervals on the same line in which the press parts 41a-41d extend in an up-down direction (select direction) in a non-connection (neutral) state.

On the right side of the shift lugs 40a to 40d, a shift shaft 50 extending in the vertical direction is provided in parallel with the arrangement of the pressing portions 41a to 41d.
The shift shaft 50 according to the present embodiment is configured by four cylindrical members 61 a to 61 d that are rotatable around each other around a central axis 60. Both ends of the central shaft 60 are fixed to support members 62 and 63. The lower ends of the cylindrical members 61a to 61d are rotatably supported by the support member 62. The upper ends of the cylindrical members 61a to 61d are expanded outward in a direction perpendicular to the central axis to form flanges 64a to 64d. Spline grooves (engaging portions) are formed in the outer peripheral edge portions of the flange portions 64a to 64d so as to extend in the vertical direction. The four flange portions 64a to 64d have the same outer diameter. The cylindrical members 61a to 61d are provided with arm portions 65a to 65d, respectively. The arm portions 65a to 65d protrude radially outward from the outer walls of the cylindrical members 61a to 61d, and are arranged so that the tips are positioned between the pair of pressing portions 41a to 41d of the shift lugs 40a to 40d. It is formed in a disc shape so as to push 41d in the front-rear direction. The four arm portions 65a to 65d are spaced apart in the select direction so as to coincide with the vertical positions of the pressing portions 41a to 41d of the four shift lugs 40a to 40d. The cylindrical members 61b to 61d excluding the first cylindrical member 61a located at the innermost portion have openings so that the arm portions 61a to 61c protruding from the inner cylindrical members 61a to 61c can move in the shift direction. 67 is provided.

  When the first cylindrical member 61a among the four cylindrical members 61a to 61d is rotated and the first shift lug 41a is moved in the shift direction from the neutral position to the shift position, the second speed gear 12 and the sixth speed gear 14 are shifted. To do. When the second cylindrical member 61b outside the first cylindrical member 61a is rotated to move the second shift lug 41b to the shift position, the first speed gear 11 and the third speed gear 13 are shifted. When the third cylindrical member 61c outside the second cylindrical member 61b is rotated to move the third shift lug 41c to the shift position, the fourth speed gear 15 and the reverse gear 17 are shifted. When the outermost fourth cylindrical member 61d is rotated to move the fourth shift lug 40d to the shift position, the fifth gear 16 is shifted.

The cylindrical members 61a to 61d are selectively rotated by a shift motor 70. The shift motor 70 is fixed to the support member 63 and rotates the cylindrical members 61 a to 61 d via the speed reduction mechanism 71 and the select shift gear 72.
The output gear 71a of the speed reduction mechanism 71 is arranged so that the axis thereof is parallel to the shift shaft 50, and a spline groove is formed so as to extend in the axial direction so as to be opposed to the central axis 60 of the shift shaft 50. Yes. As shown in FIG. 3, the select shift gear 72 is formed in an annular plate shape, and gear teeth are formed on the outer peripheral portion 72a. The outer peripheral portion 72a of the select shift gear 72 is engaged with the output gear 71a of the speed reducer 71, while the inner peripheral portion 72b can be fitted with spline grooves provided in the flange portions 64a to 64d of the cylindrical members 61a to 61d. Four such engaging teeth are formed at equal intervals in the circumferential direction. The engaging teeth of the inner peripheral portion 72b of the select shift gear 72 are set to have a narrow vertical width so that they cannot be simultaneously fitted into the spline grooves of the adjacent cylindrical members 61a to 61d. The engaging teeth of the inner peripheral portion 72b of the select shift gear 72 of this embodiment are not provided over the entire circumference and the number of teeth is four, but the number of teeth is particularly limited. What is necessary is just to set suitably. The spline grooves of the flange portions 64a to 64d of the cylindrical members 61a to 61d are formed over the entire circumference. However, if a rotation angle corresponding to the shift stroke Ss is obtained, a part of the circumferential direction is obtained. It may be provided. If spline grooves are provided over the entire circumference as in the present embodiment, it is possible to cope with even a large shift stroke Ss.

  The select shift gear 72 is arranged to be movable in the vertical direction by a select mechanism. The selection mechanism includes a ball screw 80 and a selection motor 81 that rotationally drives the ball screw 80. The screw shaft 80 a of the ball screw 80 is disposed so that the axis thereof is parallel to the shift shaft 50 relative to the upper portion of the shift shaft 50. A selection fork 82 protrudes from a nut 80b that moves up and down on the screw shaft 80a of the ball screw 80, and a tip of the selection fork 82 grips the selection shift gear 72 in a rotatable manner.

  That is, the select shift gear 72 moves up and down on the shift shaft 50 in accordance with the nut 80 b that moves up and down by the select motor 81. Therefore, the operation of the select motor 81 is controlled so that the select shift gear 72 is aligned with the vertical positions of the flange portions 64a to 64d of the desired cylindrical members 61a to 61d so that the spline grooves and the engagement teeth are fitted to each other. By driving the motor 70 and rotating the select shift gear 72, only the cylindrical members 61a to 61d fitted to the select shift gear 72 can be selectively rotated. Then, as the cylindrical members 61a to 61d rotate, the arm portions 65a to 65d rotate to push the pressing portions 41a to 41d in the shift direction, and shift the corresponding shift lugs 40a to 40d.

FIG. 4 is a reference diagram for explaining the pitch angle of the spline grooves of the cylindrical member 61a.
As shown in FIG. 4, in this embodiment, the pitch angle θp of the spline groove of the flange portion 64a of the cylindrical member 61a is further set in correspondence with the shift stroke Ss of the shift lug. Specifically, the rotation angle θs between the shift position of the pressing portion 41a and the rotation position of the arm portion 65a at the neutral position is set to coincide with the pitch angle θp of the spline grooves of the flange portions 64a to 64d. Similarly, for the other cylindrical members 61b to 61d, the pitch angle θp of the spline groove is set corresponding to the shift stroke Ss of the shift lug.

  The shift motor 70 and the select motor 81 are driven and controlled by an ECU (not shown) based on the operation of the shift lever, the operating state of the engine, and the like. The The ECU further controls the operation of the clutches 2 and 3 at the time of shifting. Specifically, when switching the gear position, the ECU connects the other clutch 3 or 2 while connecting the other clutch 3 or 2 from the state before the gear shift where the one clutch 2 or 3 is connected. Connect to the gear. Then, when the number of rotations of the next shift stage is synchronized, the previous stage is disconnected, thereby enabling a seamless shift.

  As described above, in the present embodiment, the shift shaft 50 is configured by the plurality of cylindrical members 61a to 61d, and the cylindrical members 61a to 61d are rotationally driven to rotate the arm portions 65a to 65d, thereby corresponding shift lugs 40a. ˜40d is configured to shift, so when performing a selection operation for switching the shift stage for shifting or releasing the shift, the flanges 64a to 64d of the cylindrical members 61a to 61d arranged adjacent to each other in the vertical direction It is possible only by movement between. Therefore, the select operation time can be shortened, and a quick shift can be achieved. Further, since only the select shift gear 72 moves up and down during the select operation and the shift shaft 50 does not move in the shift direction, the inertia during the select operation is reduced and the stop position accuracy in the select direction can be improved.

  In particular, in the present embodiment, the pitch angle θp of the spline groove that fits the flanges 64a to 64d and the select shift gear 72 is set corresponding to the shift stroke Ss, and the select shift is performed after the shift operation and the shift release operation. The spline groove of the gear for use 72 and the spline grooves of the flange portions 64a to 64d are configured to coincide with each other. Therefore, after the shift operation and the shift release operation, the select shift gear 72 can be moved in the select direction while maintaining the rotation angle, and can be fitted to the spline grooves of the other flange portions 64a to 64d. As a result, the select operation can be performed without the need to adjust the rotation angle of the select shift gear 72, the operation of the shift arm 65 is simplified, the control can be facilitated, and the speed change can be performed more quickly. it can.

In addition, since the vertical width of the spline of the shift gear 72 is set so that it can be locked only to one of the flange portions 64a to 64d, a plurality of shift stages are not selected at the same time, and malfunction is ensured. Can be prevented.
In the above embodiment, the pitch angle θp of the spline grooves formed in the flange portions 64a to 64d of the cylindrical members 61a to 61d is set corresponding to the shift stroke Ss. A groove may be provided, and the pitch angle of the spline groove may be set corresponding to the shift stroke Ss.

Moreover, in the said embodiment, although the upper end of the cylindrical members 61a-61d is diameter-expanded radially outward, the collar parts 64a-64d are formed, and the spline groove is formed in these collar parts 64a-64d. It is good also as a structure which forms a spline groove in the upper part of the outer peripheral wall of the cylindrical members 61a-61d.
In this embodiment, the shift lugs 40a to 40d are provided with a pair of pressing portions 41a to 41d formed in a claw shape. However, as shown in FIG. The pressing portions 41a ′ to 41d ′ may be formed in a columnar shape, the arm portions 65a ′ to 65d ′ may be bifurcated, and the pressing portions 41a ′ to 41d ′ may be positioned therebetween.

  Further, the present invention can also be applied to a transmission having a different number of shift stages from the present embodiment. The present invention can be applied not only to a dual clutch type transmission but also to a single clutch type transmission.

DESCRIPTION OF SYMBOLS 1 Transmission part 30a-30d Shift rail 40a-40d Shift lug 20, 21, 22, 23 Shift fork 50 Shift shaft 61a-61d Cylindrical member 72 Select shift gear

Claims (4)

A shift shaft provided with an arm portion projecting radially outward and having an axis line extending in the select direction;
A shift lug having a pressing portion pressed against the arm portion and arranged in a plurality in the select direction;
A shift fork connected to the shift lug via a shift rail and performing a shift operation of the shift stage,
In the transmission that moves the shift lug in the shift direction by pushing the pressing portion in the shift direction perpendicular to the select direction by the arm portion, and shifts the shift fork via the shift rail.
A gear for select shift, which is inserted into the shift shaft so as to be movable and rotatable in the select direction and formed with engagement teeth;
The shift shaft is configured by arranging a plurality of cylindrical members on the same axis,
The plurality of cylindrical members are formed with the arm portion at one end portion thereof, and with the other end portion being formed with an engagement portion that engages with an engagement tooth of the select shift gear,
The select shift gear moves in the select direction, selects a predetermined cylindrical member, rotates and engages with an engaging portion of the cylindrical member, and selectively rotates the cylindrical member, A transmission device, wherein the arm portion provided on the cylindrical member is moved in the shift direction to perform the shift operation. Each of the engaging portions of the cylindrical members or the engaging teeth of the select shift gear are formed in the circumferential direction,
The pitch angle of the plurality of engagement portions or the plurality of engagement teeth is determined by the selection shift gear that rotates the shift lug by rotating the predetermined cylindrical member while maintaining the rotation angle. 2. The transmission according to claim 1, wherein the transmission is set according to a shift stroke of the shift lug so that an engagement tooth engages with an engagement portion of another cylindrical member by moving in the direction. .   The transmission according to claim 2, wherein the engaging portion of the cylindrical member or the engaging teeth of the select shift gear is formed over the entire circumference.   The other end portion of the cylindrical member extends radially outward to form a flange portion, and the engagement portion is formed at a tip end of the flange portion. The transmission described.

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