JP5214521B2 - Gear shift device - Google Patents

Description

  The present invention relates to a transmission shift device that switches a gear position of a transmission mechanism.

When shifting from a state in which a pair of gear trains of the gear transmission mechanism is effectively transmitting power to a state in which other gear trains are effectively transmitting power, the resistance is high in the power transmission state, so the clutch is usually disconnected. The power transmission is cut off to enable switching.
Also, if the shift operation input by the shift pedal directly rotates the shift drum, the shift operation will not be performed smoothly, such as when a dog hit occurs, so a lost motion mechanism is interposed between the shift spindle and the shift drum. A good speed change operation feeling can be obtained.

  In the transmission shift device having the lost motion mechanism, a configuration for automatically controlling the stepping of the clutch is disclosed in Patent Document 1 filed earlier by the same applicant.

Japanese Patent Application No. 2008-22214

In Patent Document 1, since the lost amount of the lost motion mechanism varies, a shift restricting mechanism for restricting the rotation of the shift drum is provided on the downstream side of the lost motion mechanism.
The shift restricting mechanism restricts the rotation of the lost motion mechanism on the downstream side so as to store the operating force of the shifting operation.When the sufficient force is stored, the restriction is released and the shift drum is moved by the accumulated force. Since the gears are rotated and the gears are switched, the gear shifting operation can be performed at a predetermined timing regardless of variations in the lost amount.

  That is, in the shift shift device of Patent Document 1, when the shift pedal is fully depressed and the operation force is sufficiently stored in the lost motion mechanism, the shift control mechanism is released and the shift drum is rotated by the stored force. Then, the shift fork moves the shifter of the gear transmission mechanism, and the shift is executed by switching the dog clutch connection.

As described above, since the shifting work is executed by the force stored in the lost motion mechanism, the force stored in the lost motion mechanism must be maintained until the switching of the dog clutch connection in the gear transmission mechanism is completed. Therefore, the pilot must keep stepping on the shift pedal until the dog clutch connection is switched.
Even if the shift pedal is fully depressed, the force stored in the lost motion mechanism is lost if the shift pedal is released halfway until the dog clutch connection switching is completed.

  The present invention has been made in view of the above points. The purpose of the present invention is to input a shift operation to a necessary extent, so that the shift can be reliably executed without continuing the shift operation input, and the operability is improved. It is in the point which provides the speed-shift device which can aim at.

In order to achieve the above object, the invention according to claim 1
In the shift shift device that transmits the rotation of the shift spindle (31) by the shift operation input to the rotation of the shift drum (21) via the intermittent feed mechanism (32) and the lost motion mechanism (50) to perform a shift,
An upstream latch mechanism (70) that holds a required rotation position of the upstream rotation member (51) of the lost motion mechanism (50) rotated through the intermittent feed mechanism (32) by a shift operation input ;
A downstream latch mechanism (80) for latching and regulating the rotation of the downstream rotation member (61) integral with the shift drum (21) on the downstream side of the lost motion mechanism (50) ,
The upstream latch mechanism (70) provided on the upstream side of the lost motion mechanism (50) is formed with a latch recess (53v) corresponding to each shift stage on the outer periphery of the upstream rotation member (51), The swinging upstream latch arm (71) hooks the latch pawl (71c) at the tip to the latch recess (53v),
The downstream latch mechanism (80) has a latch recess (63v) corresponding to each gear position on the outer periphery of the downstream rotation member (61), and a swinging downstream latch arm (81) at the tip. Hook the latch claw (81c) to the latch recess (63v),
The upstream latch arm (71) and the downstream latch arm (81) have a common swing center base end (75) and are pivotally supported by a common latch arm shaft (76) as a unit. A shift shift device to be used is provided .

According to a second aspect of the invention, in the transmission shift device according to claim 1,
The common swing center base end (75) is moved in the axial direction by the actuator (91), and the latch claws (71c, 81c) of the upstream latch arm (71) and the downstream latch arm (81) A latching function switching mechanism (90) that disables latching with the corresponding latch recess (53v, 63v) is provided.

According to a third aspect of the present invention, in the shift shift device according to the first or second aspect ,
The upstream rotating member (51) of the lost motion mechanism (50) is provided with a stopper mechanism (59) that prohibits the rotation from the minimum gear to the lower gear and the rotation from the maximum gear to the upper gear. It is characterized by.

According to the shift shift device of the first aspect, the upstream side rotation member (51) of the lost motion mechanism (50) rotated from the shift spindle (31) via the intermittent feed mechanism (32) by a shift operation input. Equipped with an upstream latch mechanism (70) that holds the required rotation position, there is a necessary shift operation input, and the required rotation position of the upstream rotation member (51) of the lost motion mechanism (50) is maintained. If this is done, operating force can be stored and maintained in the lost motion mechanism (50), and even if the shift operation input is stopped and the shift spindle (31) is returned before the shift speed is changed, the lost motion mechanism (50) The shift drum (21) can be rotated and the shift can be reliably performed without continuing the shift operation input by the stored and maintained force, and the operability can be improved.

The downstream motion mechanism (50) is equipped with a downstream latch mechanism (80) that locks and regulates the rotation of the shift drum (21) on the downstream side of the lost motion mechanism (50). By sufficiently storing and releasing the latch of the downstream side latch mechanism (80) in a timely manner, the shift drum (21) can be reliably rotated and the shift stage can be switched reliably.

  The downstream latch mechanism (80) has a latch recess (63v) corresponding to each gear position formed on the outer periphery of the downstream rotation member (61) of the lost motion mechanism (50), and swings the downstream latch arm ( 81) hooks the latch pawl (81c) at the tip into the latch recess (63v), and the upstream latch mechanism (70) provided on the upstream side of the lost motion mechanism (50) is connected to the upstream rotating member (51). Latch recesses (53v) corresponding to the respective speeds are formed on the outer periphery of the upper side, and the swinging upstream latch arm (71) hooks the latch pawl (71c) at the tip of the latch recess (53v) to the upstream side. The latch arm (71) and the downstream latch arm (81) have a common swing center base end (75) and are pivotally supported by a common latch arm shaft (76) as a single unit. The downstream latch mechanism (80) unlocks the downstream rotation member (61) in conjunction with the operation in which the upstream latch mechanism (70) latches and holds the upstream rotation member (51). So The shift drum (21) is rotated to perform a shift, and if there is a required shift operation input, the shift can be reliably executed.

According to the shift shift device of the second aspect, the upstream swing arm (71) and the downstream latch arm (81) are moved by moving the common swing center base end portion (75) in the axial direction by the actuator (91). The latch pawls (71c, 81c) and the corresponding latch recesses (53v, 63v) are equipped with a latching function switching mechanism (90) that disables the latching (53v, 63v). When the latching function switching mechanism (90) switches the both latching function to the enabled state, there is a necessary shift operation input. Therefore, the shift can be reliably performed, and the rotation position of the shift drum (21) is always in any one of the shift positions, and the rotation is not stopped at the neutral position.
Therefore, by setting the latching function switching mechanism (90) to the state in which both latching functions are enabled during traveling, setting of the shift drum (21) to the neutral position is prevented, and the operator can set the shift drum (21) to the neutral position. There is no need to pay attention to the speed change operation so that the position is not set, and the operability is excellent.

According to the shift shift device of the third aspect, the upstream side rotation member (51) of the lost motion mechanism (50) is prohibited from rotating from the minimum shift stage to the lower stage and from the maximum shift stage to the upper stage. Since the stopper mechanism (59) is provided, it cannot be operated if the operator tries to perform a shift operation below the minimum shift stage and above the maximum shift stage, so that the current shift stage is the minimum shift stage or the maximum shift stage. Can be sensed.

1 is a cross-sectional view of a transmission for a motorcycle according to the present embodiment. It is sectional drawing of this transmission shift apparatus. It is a partial exploded sectional view of the same shift device. It is a left view of a master arm. It is a left view of a shift input member. It is a left view of the upstream rotation member of a lost motion mechanism. It is a left view of the downstream rotation member of a lost motion mechanism. It is a side view which shows each principal part of the gear shift device of the state where one gear stage was established, respectively. It is a side view which shows each principal part of the same speed shift device of the 1 process of changing according to speed change operation input, respectively. It is a side view which shows each principal part of the same shift apparatus of the next process, respectively. It is a side view which shows each principal part of the same shift apparatus of the next process, respectively. It is a side view which shows each principal part of the same gear shift device of the change end process of the next gear stage. It is a side view which shows each principal part of the same shift apparatus of the next shift complete state.

Hereinafter, an embodiment according to the present invention will be described with reference to FIGS.
FIG. 1 is a cross-sectional view of a transmission for a motorcycle according to the present embodiment.
A transmission chamber 2 is formed in an engine case 1 of an internal combustion engine mounted on a motorcycle with a crankshaft oriented in the vehicle body width direction (left-right direction), and a gear transmission mechanism 10 of the transmission is configured in the transmission chamber 2. Has been.

A main shaft 11 that is a speed change input shaft and a counter shaft 12 that is an output shaft are directed to the left and right side walls of the engine case 1 forming the speed change chamber 2 so as to be rotatable through bearings 13 and 14, respectively. It is pivotally supported.
A gear transmission mechanism 10 is configured between the main shaft 11 and the counter shaft 12 that are parallel to each other.

  On the main shaft 11, from the right to the left, a first speed drive gear m1, a fifth speed drive gear m5, a fourth speed drive gear m4, a third speed drive gear m3, a sixth speed drive gear m6, and a second speed drive gear m2 are arranged in order. The first-speed drive gear m1 is formed integrally with the main shaft 11, and the fifth-speed drive gear m5 is an idle gear that is rotatably supported by the main shaft 11. The fourth-speed drive gear m4 and the third-speed drive gear m3 Is a shifter gear that is integrally formed and is spline-fitted to the main shaft 11. The sixth speed drive gear m6 is an idle gear that is rotatably supported on the main shaft 11, and the second speed drive gear m2 is connected to the main shaft 11. It is mated.

  On the other hand, on the counter shaft 12, the 1st speed driven gear n1, the 5th speed driven gear n5, the 4th speed driven gear n4, the 3rd speed driven gear n3, the 6th speed driven gear n6, and the 2nd speed driven gear n2 are arranged in order from right to left. The first-speed driven gear n1 is an idle gear that is rotatably supported on the counter shaft 12, the fifth-speed driven gear n5 is a shifter gear that is spline-fitted to the counter shaft 12, and the fourth-speed driven gear n4 The third speed driven gear n3 is an idle gear that is rotatably supported on the counter shaft 12, and the sixth speed driven gear n6 is a shifter gear that is spline-fitted to the counter shaft 12, and the second speed driven gear n2 is a counter shaft 12 It is an idle gear that is rotatably supported by the shaft.

The gear transmission mechanism 10 is a constantly meshing transmission gear mechanism, and the corresponding driving gear and driven gear are always meshed.
An integral third speed drive gear m3 and fifth speed driven gear n5 which are shifter gears on the main shaft 11 and a fifth speed driven gear n5 and sixth speed driven gear n6 which are shifter gears on the counter shaft 12 are moved in the axial direction and adjacent to each other. When the dog clutches of the gears to be engaged come into contact with each other, any one of the gear trains (meshing between the drive gear and the driven gear) effectively transmits power, so that one gear is established, and the established gear Power is transmitted from the main shaft 11 to the counter shaft 12 by the ratio.
The gear transmission mechanism 10 has a neutral position where all gear trains are invalid and power is not transmitted.

Power of a crankshaft (not shown) of the internal combustion engine is transmitted to the main shaft 11, and a multi-plate friction clutch 3 that connects and disconnects power transmission is interposed therebetween.
Power is transmitted from the crankshaft to the clutch outer 3 o of the multi-plate friction clutch 3 through the primary gear train 4 and the torque damper 5.

In the multi-plate friction clutch 3, a clutch inner 3i is fitted to the right end of the main shaft 11, and the clutch outer 3o rotatably supported on the main shaft 11 covers the outer periphery of the clutch inner 3i. In the meantime, the driving friction plate 3oo that is spline-fitted to the clutch outer 3o and the driven friction plate 3ii that is spline-fitted to the clutch inner 3i are alternately overlapped in the axial direction, and the pressure receiving plate 3ip formed on the left clutch inner 3i and the right side It is sandwiched between a pressure plate 3p that is slidably supported in the axial direction by the clutch inner 3i.
The pressure plate 3p is urged leftward by the clutch spring 3s.

The main shaft 11 has a cylindrical shape, and the push rod 6 passes through the inside thereof. The right end of the push rod 6 protruding rightward from the main shaft 11 is connected to the pressure plate 3p via the release member 7. .
On the other hand, the left end portion of the push rod 6 passes through the engine case 1 and is fitted to the piston 8 p of the slave hydraulic cylinder 8.

The slave hydraulic cylinder 8 is driven by a master hydraulic cylinder controlled by the ECU.
Therefore, when the slave hydraulic cylinder 8 is actuated and the piston 8p pushes the push rod 6 to the right, the pressure plate 3p is moved to the right against the spring force of the clutch spring 3s via the release member 7. The multi-plate friction clutch 3 connected by the spring force of the spring 3s can be disconnected.

  When the gear shift mechanism 10 switches the shift stage by moving the shifter gear, the dog clutch is stepped. However, if power is transmitted from the main shaft 11 to the counter shaft 12, a large resistance is applied to the dog clutch disconnection. Accordingly, since smooth shifting cannot be performed, it is necessary to disconnect the multi-plate friction clutch 3 to cut off power transmission.

  The counter shaft 12, which is an output shaft, has a drive sprocket 15 fitted to the left end penetrating the engine case 1 to the left, and the gear stage output established by the gear transmission mechanism 10 is output from the drive sprocket 15 via the chain 16. To travel to the rear wheels.

A shift shift device 20 that shifts the shifter gear of the gear transmission mechanism 10 to perform a shift will be described below.
The shift shift device 20 has shift forks 24, 25, and 26 slidably supported on the shift fork shafts 22 and 23 formed on the outer peripheral surface of the shift drum 21 by rotating the shift drum 21. The shift fork 26 is moved in the axial direction by being guided by the shift groove 21v, and the shift fork 26 is moved integrally with the shift gears 3 and 4 which are splined to the main shaft 11, and the shift fork 24 is countered. The fifth-speed driven gear n5, which is a shifter gear that is spline-fitted to the shaft 12, is moved, and the shift fork 25 moves the sixth-speed driven gear n6, which is a shifter gear, to change the gear position.

The shift drum 21 of the transmission shift device 20 is rotated by the operator operating the shift pedal 30 with his / her foot.
A mechanism in which the operating force of the shift pedal 30 in the transmission shift device 20 is transmitted to the rotation of the shift drum 21 will be described with reference to FIGS.

The shift pedal 30 is fitted to the left end of the shift spindle 31 protruding leftward from the engine case 1, and the shift spindle 31 is rotated by the swinging operation of the shift pedal 30.
A master arm 33 of an intermittent feed mechanism 32 is fitted to the shift spindle 31 and swings integrally with the shift spindle 31.

  As shown in FIGS. 3 and 4, the master arm 33 has a vertically long plate shape, the shift spindle 31 is inserted through the circular hole 33a at the base end, and is bent into a long and narrow predetermined shape on the distal end side. A cam hole 33b is formed, and a drive hole 33c is formed in a convex shape between the base end circular hole 33a and the distal end cam hole 33b. The drive hole 33c has a sharp angle with the direction from the circular hole 33a toward the drive hole 33c. A rectangular restriction hole 33d is formed in an angled direction, and an end in the direction from the circular hole 33a to the restriction hole 33d is bent to form a locking piece 33e.

The cam hole 33b includes a central arc portion 33ba centering on the base end circular hole 33a, inclined portions 33bb and 33bb on both sides thereof, and end arc portions 33bc and 33bc centering on the circular holes 33a on both sides thereof.
Further, the convex drive hole 33c is a portion where a long hole that is long in the radial direction from the center of oscillation of the base end is particularly effective.

Referring to FIGS. 2 and 8 (a), the coil portions of the return spring 34 are wound around the shift spindle 31 fitted through the circular hole 33a of the master arm 33, and both end portions extending in the same direction. Is attached so as to sandwich the locking piece 33e of the master arm 33 from the outside.
A cylindrical pin 36 protruding leftward from a predetermined position of a guide plate 35 fixedly disposed inside the master arm 33 passes through a rectangular restriction hole 33d of the master arm 33, and the return spring 34 It protrudes between the both ends extended in the same direction from the coil part, and is made to pinch | interpose into both ends (refer Fig.8 (a)).

  Accordingly, the cylindrical pin 36 protruding from the guide plate 35 and the locking piece 33e of the master arm 33 between both ends extending in the same direction from the coil portion of the return spring 34 having the coil portion wound around the shift spindle 31. Will be sandwiched.

When the cylindrical pin 36 and the locking piece 33e are in the same direction from the shift spindle 31, the master arm 33 is in the neutral position, and when the shift pedal 30 is depressed, the shift spindle 31 rotates and the master arm 33 moves in either direction. The cylindrical pin 36 presses one end of the return spring 34 and the locking piece 33e of the master arm 33 pushes against the spring force to open the other end. The urging force that tries to return to the position works.

Accordingly, when the depression of the shift pedal 30 is stopped and the operating force acting on the master arm 33 via the shift spindle 31 is lost, the master arm 33 is returned to the original neutral position together with the shift pedal 30 by the return spring 34.
The swing of the master arm 33 is restricted within the range of the restriction hole 33d through which the cylindrical pin 36 passes.

The right end is fitted into the left end portion of the shift drum 21 pivotally supported at both ends of the engine case 1 via bearings 27, 27, and the shift drum shaft 37 is integrally projected to the left, and the shift drum shaft 37 is shifted. Located on the rotation center axis of the drum 21 and parallel to the shift spindle 31 and positioned close to each other.
A shift input member 38 is pivotally supported on the left end portion of the shift drum shaft 37 adjacent to the master arm 33 so as to be relatively rotatable.
The shift input member 38 passes through the guide plate 35.

As shown in FIGS. 3 and 5, the shift input member 38 has a shaft hole 38 a through which the shift drum shaft 37, which is the rotation center, passes, and is eccentric from the shaft hole 38 a of the left portion 38 l from the guide plate 35. A follower projection 38b protrudes to the left (see FIG. 3), and an annular sliding member 39 is fitted on the follower projection 38b and slidably fitted into the drive hole 33c of the master arm 33 (see FIG. 3). (See FIG. 2).
Since the driven projection 38b is fitted into a long hole extending in the radial direction of the drive hole 33c of the master arm 33 through the annular sliding member 39, when the master arm 33 is swung, it is driven by the swinging drive hole 33c. The projection 38 b is guided and the shift input member 38 rotates about the shift drum shaft 37.

A pair of poles 41, 41 of a pole ratchet mechanism 40 are mounted symmetrically with each other on the right side portion 38r of the guide plate 35 of the shift input member 38 so as to be swingable and swingable. A pair of springs 42 and 42 are provided to project and urge the tip of 41 toward the centrifugal side.

A lost motion mechanism 50 is interposed between the shift input member 38 and the shift drum 21 on the shift drum shaft 37.
The lost motion mechanism 50 has a lost motion between an upstream rotating member 51 rotatably supported on the shift drum shaft 37 and a downstream rotating member 61 integrally supported on the shift drum shaft 37. A motion spring 60 is interposed.

Referring to FIGS. 3 and 6, the upstream side rotation member 51 has an upstream (left side) large-diameter cylindrical part 51b and a downstream (right side) small-diameter cylindrical part 51s continuously formed coaxially, and has a small diameter. A shift drum shaft 37 passes through the cylindrical portion 51s and is rotatably supported.
Six inner circumferential recesses 51bh are formed at equal intervals in the circumferential direction on the inner circumferential surface of the large diameter cylindrical portion 51b, and the right side portion 38r of the shift input member 38 is inserted inside the large diameter cylindrical portion 51b. Then (see FIG. 2), the tip of the pair of poles 41, 41 urged to the centrifugal side by the springs 42, 42 of the pole ratchet mechanism 40 is pressed against the inner peripheral surface of the large-diameter cylindrical portion 51b. The mechanism 40 is configured (see FIG. 8B).

  That is, each pole 41 of the pole ratchet mechanism 40 is rotated in one direction by the shift input member 38, and the raised tip is hooked on one of the hooking surfaces facing the circumferential direction of the inner circumferential recess 51bh. The moving member 51 is rotated. However, when the rotating member 51 rotates in the other direction, the tip is pulled out of the inner circumferential recess 51bh and the upstream rotating member 51 is not rotated.

  Therefore, when the shift input member 38 rotates by a predetermined angle in either direction due to the swinging of the master arm 33, a pair of poles 41 pressed against the inner peripheral surface of the large-diameter cylindrical portion 51b of the upstream-side rotating member 51, The tip of one of the poles 41 protrudes into the inner peripheral recess 51bh and engages with the engaging surface of the inner peripheral recess 51bh to rotate the upstream rotating member 51, and then the master arm 33 returns to the original neutral position. When the return shift input member 38 rotates in the opposite direction, the pole 41 that has been engaged with the inner circumferential recess 51bh comes out of the inner circumferential recess 51bh, leaving the upstream rotation member 51 as it is, and the upstream rotation member 51 Intermittent feed is executed.

As shown in FIG. 6, the upstream flower cam 52 is integrally fitted on the left side and the latch flange 53 is integrally formed on the right side of the outer peripheral surface of the large-diameter cylindrical portion 51b of the upstream side rotation member 51. Has been.
The upstream-side flower cam 52 is formed with a predetermined uneven cam surface in which an upstream detent recess 52v corresponding to each of the first to sixth speeds and the neutral position is sequentially formed in the circumferential direction.

The upstream latch flange 53 is formed with upstream latch recesses 53v corresponding to the respective shift speeds by cutting out the outer peripheral edge at intervals of the central angle of 60 degrees.
In the upstream latch recess 53v, the engaging surface facing in the circumferential direction is formed at an acute angle of slightly less than 90 degrees with respect to the bottom surface.

Further, in the upstream side rotation member 51, a locking pin 54 protrudes axially rightward from a predetermined position on the right side surface of the upstream side latch flange portion 53, and further to the first speed and the sixth speed of the upstream side flower cam 52. Stopper pieces 55 protrude in the radial direction from positions between the corresponding upstream detent recesses 52v, 52v.

  On the other hand, the downstream side rotation member 61 of the lost motion mechanism 50 has a flat bottomed cylindrical shape with reference to FIG. 3 and FIG. 7, and a shaft hole 61a is drilled in the bottom wall. The downstream side flower cam 62 is integrally formed on the right side, and the downstream side latch flange portion 63 is integrally formed on the left side.

The downstream flower cam 62 is formed with a predetermined concavo-convex cam surface in which downstream detent recesses 62v corresponding to the respective first and sixth speeds and the neutral position are sequentially formed in the circumferential direction.
The downstream latch flange 63 is formed with downstream latch recesses 63v corresponding to the respective shift speeds by cutting out the outer peripheral edge at intervals of a central angle of 60 degrees.

In the downstream latch recess 63v, the engaging surface facing in the circumferential direction is formed at an obtuse angle of slightly over 90 degrees with respect to the bottom surface.
In the downstream rotation member 61, a locking pin 64 protrudes axially leftward from a predetermined position on the left side surface of the downstream flower cam 62.

In this downstream side rotation member 61, a shift drum shaft 37 is inserted from the left side into a shaft hole 61a drilled in the bottom wall (see FIG. 3), and as shown in FIG. A flange 37f formed in the middle of the shift drum shaft 37 presses the bottom wall of the downstream rotation member 61 between the shift drum 21 and a shaft hole that is drilled at the rotation center at the left end of the drum 21. The downstream rotating member 61 and the shift drum 21 are integrally coupled together with the shift drum shaft 37.
The bearing 27 that rotatably supports the shift drum 21 also supports the downstream rotation member 61 (see FIG. 2).

  A coil portion of a lost motion spring 60, which is a torsion coil spring, is wound around the small-diameter cylindrical portion 51s of the upstream-side rotation member 51 that is rotatably supported by the shift drum shaft 37, and the right end of the small-diameter cylindrical portion 51s. The portion is inserted into the cylinder of the downstream rotation member 61, and the locking pin 54 protruding to the right of the upstream rotation member 51 and the locking pin 64 protruding to the left of the downstream rotation member 61, Both end portions extending in the radial direction from the coil portion of the lost motion spring 60 are elastically squeezed and locked (see FIGS. 2 and 8C).

Since the locking pin 54 of the upstream side rotation member 51 and the locking pin 64 of the downstream side rotation member 61 are slightly displaced in the radial direction, the lost motion spring 60 is moved in the same direction from the shift drum shaft 37. The relative rotation of the upstream side rotation member 51 and the downstream side rotation member 61 is elastically suppressed by the lost motion spring 60 by being elastically sandwiched between both ends.
Therefore, the rotation of the upstream rotation member 51 constitutes the lost motion mechanism 50 that is transmitted to the downstream rotation member 61 via the elastic force of the lost motion spring 60.

As shown in FIG. 8 (b), a torsion spring is supported on the concavo-convex cam surface of the upstream flower-shaped cam 52 of the upstream rotating member 51 in the lost motion mechanism 50 so that the base end is pivotably supported by the support shaft 56p. An upstream detent mechanism 56 is configured by pressing a roller 58 rotatably supported at the tip of an upstream detent arm 57 biased by (not shown).
Therefore, the upstream detent mechanism 56 positions the upstream rotation member 51 at the rotation position where the roller 58 is accommodated in the upstream detent recess 52 corresponding to each gear position on the concave and convex cam surface of the upstream flower cam 52.

Further, as shown in FIG. 8C, a torsion spring (not shown) is pivotally supported on the concave and convex cam surface of the downstream flower cam 62 of the downstream rotating member 61 so that the base end of the downstream cam 66 can swing freely. The downstream detent mechanism 66 is configured by pressing a roller 68 pivotally supported on the tip of the downstream detent arm 67 biased by
Therefore, the downstream detent mechanism 66 positions the downstream rotation member 61 at the rotation position where the roller 68 is accommodated in the downstream detent recess 62 corresponding to each gear position and neutral position of the concave and convex cam surface of the downstream flower cam 62. The

  Referring to FIG. 8 (b), the upstream rotation member 51 has a radial direction from a position between the upstream detent recesses 52v and 52v corresponding to the first speed and the sixth speed of the upstream flower cam 52, respectively. The stopper piece 55 protrudes from the right side of the guide plate 35, and the stopper piece 55 contacts the two stopper pins 59, 59 projecting from predetermined positions on both sides of the roller 58 at the tip of the upstream detent arm 57 on the right side surface. By contacting, the upstream side rotation member 51 is restricted from rotating within a predetermined rotation angle range (a rotation angle range corresponding to the first speed to the sixth speed).

That is, the upstream side rotation member 51 is rotated and positioned by the upstream detent mechanism 56 at each speed stage from the 1st speed to the 6th speed, but 1 by the stopper mechanism of the stopper piece 55 and the stopper pins 59 and 59. Rotation from the lower speed (minimum speed) to the lower speed and rotation from the sixth speed (maximum speed) to the upper speed are prohibited.

  Next, the upstream latch mechanism 70 in which the upstream latch arm 71 is engaged with the upstream latch recess 53v of the upstream pivot member 51 and the downstream latch arm 81 in the downstream latch recess 63v of the downstream pivot member 61 are connected. The downstream latch mechanism 80 to be latched will be described.

Referring to FIGS. 2 and 8, upstream latch arm 71 and downstream latch arm 81 have a common swing center base end portion 75, and the swing center base end portion 75 is connected to engine case 1. The guide plate 35 is pivotally supported by a latch arm shaft 76 which is installed in the guide plate 35 so as to be slidable in the left and right direction.
Accordingly, the upstream latch arm 71 and the downstream latch arm 81 are pivotally supported integrally around the latch arm shaft 76.

The rocking center base end portion 75 is sandwiched by C-shaped retaining rings 77, 77 at a predetermined position of the latch arm shaft 76, and the relative movement in the axial direction with respect to the latch arm shaft 76 is restricted, and relative rotation is allowed. Are supported.
Therefore, the upstream side latch arm 71 and the downstream side latch arm 81 that share the swing center base end portion 75 together with the latch arm shaft 76 move in the axial direction (left-right direction) together.

  When the upstream latch arm 71 and the downstream latch arm 81, which are integrally formed with the swing center base end portion 75 in common, are at a predetermined position on the left side in the axial direction, the upstream latch arm 71 Extending from the right end portion of the end portion 75 toward the outer periphery of the upstream side latch flange portion 53 of the upstream side rotation member 51, the tip thereof being bent toward the upstream side latch flange portion 53 side to form a latch claw 71c, A latch pawl 71c can be hooked in an upstream latch recess 53v formed in the upstream latch flange 53 (see FIG. 8B).

  The latch claw 71c is formed to be widened from the bent portion to the tip, and when the latch claw 71c is hooked on the hooking surface formed at an acute angle of the upstream latch recess 53v, both are hooked and the upstream latch recess 53v is released. As long as the upper latch arm 71 is not pivoted, the latch is not released.

  Similarly, the downstream latch arm 81 is once bent rightward in the axial direction from the right end of the swing center base end 75 and then directed toward the outer periphery of the downstream latch flange 63 of the downstream rotating member 61. A latch claw 81c is formed projecting toward the downstream latch flange portion 63 in the middle thereof, and the latch claw 81c can be hooked in a downstream latch recess 63v formed in the downstream latch flange portion 63 ( (Refer FIG.8 (c)).

The upstream latch arm 71 and the downstream latch arm 81 extending from the common rocking center base end portion 75 are separated from each other in the axial direction (see FIG. 2), and are viewed from the left side (in the axial direction). And extend in a direction substantially perpendicular to each other (see FIG. 8A).
The upstream latch arm 71 is located on the left in the axial direction, and the downstream latch arm 81 is located on the right in the axial direction.

  The upstream latch arm 71 and the downstream latch arm 81 extend substantially perpendicular to each other so as to sandwich the upstream pivot member 51 and the downstream pivot member 61 in the axial direction, so the upstream latch arm 71 When the latch claw 71c is latched in the upstream latch recess 53v, the downstream latch arm 81 is released from the latch claw 81c in the downstream latch recess 63v. When the latch claw 81c is latched to the downstream latch recess 63v, the upstream latch arm 71 is released from the latch claw 71c latched to the upstream latch recess 53v.

That is, when one of the upstream latch mechanism 70 and the downstream latch mechanism 80 is latched, the other is in a relationship of releasing the latch.
However, when the latching state changes, it temporarily occurs that the upstream latch mechanism 70 and the downstream latch mechanism 80 are simultaneously latched.
As shown in FIGS. 8A and 8C, the downstream latch arm 81 of the downstream latch mechanism 80 is in the downstream state in which the latch pawl 81c is released from the downstream latch recess 63v and is rocked. A latch angle sensor 95, which is a limit switch for detecting the tip of the side latch arm 81, is disposed at a predetermined position.

The detection of the latch angle sensor 95 is also to detect a state in which the latch claw 71c of the upstream latch arm 71 is engaged with the upstream latch recess 53v of the upstream rotation member 51.
The detection signal of the latch angle sensor 95 is input to the ECU and is used for drive control of the slave hydraulic cylinder 8 to disconnect the multi-plate friction clutch 3.
Note that a locking pin 72 projects leftward from a predetermined position on the left side surface of the upstream latch arm 71.

  When the integrally formed upstream latch arm 71 and downstream latch arm 81 are at a predetermined position on the left side, the latch pawl 71c of the upstream latch arm 71 and the latch pawl 81c of the downstream latch arm 81 are respectively upstream. The upstream latch recess 53v of the side rotation member 51 and the downstream latch recess 63v of the downstream rotation member 61 can be hooked (state shown by a solid line in FIG. 2).

  When the upstream side latch arm 71 and the downstream side latch arm 81 move to the right from this state, the upstream side latch arm 71 and the downstream side latch arm 81 are moved to the upstream side latch recess 53v and the downstream side of the upstream side rotation member 51, respectively. 2 is disengaged in the axial direction from the downstream latch recess 63v of the moving member 61, and is unable to be engaged with the upstream latch recess 53v of the upstream rotation member 51 and the downstream latch recess 63v of the downstream rotation member 61 (FIG. 2). In the state indicated by a two-dot chain line).

The latch arm shaft 76 that pivotally supports the upstream latch arm 71 and the downstream latch arm 81 protrudes to the left through the guide plate 35, and the base end portion of the leading arm 85 rotates around the protruding left shaft portion. It is supported so as to be movable and movable in the axial direction (see FIGS. 2 and 8).
A follower pin 86 projects leftward from the leading end of the leading arm 85, and the follower pin 86 is slidably fitted into a cam hole 33b bent into a predetermined shape of the master arm 33.
Therefore, when the master arm 33 swings, the cam hole 33b that turns at the leading end of the swing guides the driven pin 86 and swings the leading arm 85.

The leading arm 85 extends from the latch arm shaft 76 in the same direction along the upstream latch arm 71, and includes a locking pin 87 protruding rightward from a position near the base end of the right side surface of the leading arm 85. The locking pin 72 protruding to the left of the upstream latch arm 71 overlaps in the axial direction.
A torsion coil spring 88 is provided around the outer periphery of the common swing center base end portion 75 of the upstream latch arm 71 and the downstream latch arm 81 so as to wind the coil portion. Both end portions extending in the radial direction from the coil portion of the torsion coil spring 88 are elastically squeezed and locked to the locking pin 72 of the upstream latch arm.

Since the locking pin 87 of the leading arm 85 and the locking pin 72 of the upstream side latch arm 71 are at slightly different distances from the latch arm shaft 76, the latch pin 87 is connected to both ends of the torsion coil spring 88 in the same direction. The relative rotation of the leading arm 85 and the upstream latch arm 71 is suppressed by the torsion coil spring 88 by the spring force.
Therefore, the swing of the leading arm 85 is transmitted to the upstream latch arm 71 (and the integrated downstream latch arm 81) via the torsion coil spring 88.

An electromagnetic solenoid 91 is provided at the left end of the latch arm shaft 76 that pivotally supports the leading arm 85 with a drive shaft 91d connected coaxially.
A compression coil spring 92 is wound around the left end portion of the latch arm shaft 76 to urge the latch arm shaft 76 to the right.

  When the electromagnetic solenoid 91 is demagnetized, the latch arm shaft 76 is urged to the right by the compression coil spring 92 to be in a predetermined position on the right side, and the upstream latch arm 71 and the downstream latch arm 81 are respectively upstream. The upstream latch recess 53v of the side pivot member 51 and the downstream latch recess 63v of the downstream pivot member 61 are disengaged in the axial direction, and cannot be hooked (a state indicated by a two-dot chain line in FIG. 2).

  When the electromagnetic solenoid 91 is excited and the drive shaft 91d is pulled, the latch arm shaft 76 moves to the left together with the upstream latch arm 71 and the downstream latch arm 81 against the compression coil spring 92, and both latch claws 71c. , 81c are in a predetermined position on the left side where they can be engaged with the upstream latch recess 53v of the upstream rotation member 51 and the downstream latch recess 63v of the downstream latch arm 81 (a solid line in FIG. 2). State shown).

As described above, the latching function switching mechanism 90 that switches both latching functions of the upstream side latch mechanism 70 and the downstream side latch mechanism 80 to the disabled state or the enabled state by the drive control of the electromagnetic solenoid 91 is configured.
As the upstream latch arm 71 and the downstream latch arm 81 move, the torsion coil spring 88 wound around the swing center base end portion 75 also moves together.

This latching function switching mechanism 90 is controlled to switch between running and stopping.
When traveling, the electromagnetic solenoid 91 is energized to enable the upstream latch mechanism 70 and the downstream latch mechanism 80 to be in the latching function state, so that the shift stage can be smoothly switched, and the neutral position is set to the downstream detent mechanism 66. Even if there is a downstream detent recess 62v corresponding to, neither the upstream latch recess 53v nor the downstream latch recess 63v has a neutral position, and when one of the upstream latch recess 53v and the downstream latch recess 63v is engaged, the other is Since the latch is released, the shift drum 21 is not set to the neutral position regardless of how the driver performs a shift operation during traveling.

  In addition, when the vehicle is stopped, the electromagnetic solenoid 91 is demagnetized so that the upstream latch mechanism 70 and the downstream latch mechanism 80 are disabled, so that either the upstream latch mechanism 70 or the downstream latch mechanism 80 is locked. Therefore, the upstream detent mechanism 56 and the downstream detent mechanism 66 can be positioned by pressing the rollers 58 and 68 into the respective detent recesses 52v and 62v corresponding to the neutral position, and the shift drum 21 can be easily moved to the neutral position. Can be set to

The present gear shift device 20 is configured as described above, and the gear shift step will be described step by step with reference to FIGS.
It should be noted that in the following shift speed changing process, the upstream latch mechanism 70 and the downstream latch mechanism 80 are in a state in which the latching function is possible.

FIG. 8 shows a state in which one shift speed is established. FIG. 8A is a left side view of the entire shift shift device 20, and FIG. 8C is a left side view mainly showing the upstream side rotation member 51, and FIG. 8C is a left side mainly showing the downstream side rotation member 61 while further omitting a part of the transmission shift device 20. FIG. FIG. 8A, FIG. 8B and FIG. 8C all show the same state.
FIGS. 9 to 13 also illustrate one state that changes over time in the above-described drawings (a), (b), and (c).

  First, in FIG. 8 showing a state in which one shift stage is established, the shift pedal 30 is not depressed, the master arm 33 is in the neutral position, and the downstream latch mechanism 80 has the latch latch 81c on the downstream side. The shift member 61 is engaged with the downstream latch recess 63v (upstream latch mechanism 70 is released), and the shift drum 21 is constrained to the rotation angle position of the shift step to establish the shift step. The driven pin 86 at the tip of the leading arm 85 is positioned at the center of the central arc portion 33ba of the cam hole 33b of the master arm 33.

FIG. 9 shows a state at the time when the shift pedal 30 is depressed in one direction from the state where the gear stage is established, and the master arm 33 swings slightly less than 4 degrees against the return spring 34 via the shift spindle 31. Show.
In this example, the master arm 33 swings counterclockwise in FIG.
In this specification, the directions of swinging or turning are described as clockwise (clockwise) and counterclockwise (counterclockwise) with reference to the left side of FIGS.
The driven pin 86 at the tip of the leading arm 85 reaches the end of the central arc portion 33ba of the cam hole 33b of the master arm 33, but during that time, the central arc portion 33ba is in the same position without acting, so that the leading arm 85 swings. Does not move.

  The driven projection 38b slidably fitted in the drive hole 33c of the master arm 33 is guided to rotate the shift input member 38, and one pole 41 of the pole ratchet mechanism 40 is connected to the inner circumference of the upstream side rotation member 51. The upstream side rotating member 51 is hooked on the hooking surface of the recess 51bh and rotates the upstream side rotating member 51 counterclockwise by about 15 degrees, but the downstream side rotating member 61 connected by the lost motion spring 60 of the lost motion mechanism 50 is Although the rotation is slightly performed, the latch claw 81c of the downstream latch arm 81 is engaged with the engagement surface of the downstream latch recess 63v and the rotation is restricted, so that the operating force is stored in the lost motion spring 60.

Next, FIG. 10 shows a state when the master arm 33 swings and swings slightly less than 8 degrees.
Since the driven pin 86 at the tip of the leading arm 85 has moved to the inclined portion 33bb of the cam hole 33b of the master arm 33, the leading arm 85 swings clockwise as guided by the inclined portion 33bb, and the torsion coil spring 88 The upstream latch arm 71 is swung in the same direction via the master arm 33, but the upstream rotation member 51 is further rotated to about 30 degrees via the shift input member 38 due to the swing of the master arm 33. The upstream latch arm 71 abuts the latch pawl 71c at the front end against the upstream latch flange portion 53 to prevent the upstream latch arm 71 (and the downstream latch arm 81) from swinging (see FIG. 10B). Therefore, the latching state of the downstream rotating member 61 by the downstream latch arm 81 is maintained.

  Therefore, the operating force is further stored in the lost motion spring 60 of the lost motion mechanism 50, and the force is also stored in the torsion coil spring 88 between the leading arm 85 and the upstream latch arm 71.

Next, FIG. 11 shows a state when the master arm 33 swings and swings about 12 degrees.
The driven pin 86 at the leading end of the leading arm 85 reaches the end of the inclined portion 33bb of the cam hole 33b of the master arm 33, and is immediately after the most force is stored in the torsion coil spring 88. The side rotation member 51 is further rotated to about 50 degrees, and the upstream latch arm 71 is stored in the torsion coil spring 88 with the leading latch claw 71c facing the upstream latch recess 53v from the upstream latch flange 53. The latch pawl 71c is pivoted clockwise by the force and is latched on the latching surface of the upstream latch recess 53v, but the latch pawl 81c of the downstream latch arm 81 pivoted integrally is formed on the downstream pivot member 61. Immediately before coming out of the downstream latch recess 63v, the latch has not yet been released, so the downstream rotating member 61 on which the operating force stored in the lost motion spring 60 of the lost motion mechanism 50 acts still rotates. do not do.

  The downstream rotating member 61 is slightly rotated while the latch claw 81c of the downstream latch arm 81 slides in contact with the latching surface of the downstream latch recess 63v.

Next, FIG. 12 shows a state when the depression of the shift pedal 30 reaches the limit and the master arm 33 swings about 15 degrees which is the limit regulated by the regulation hole 33d.
The leading pin 86 of the leading end of the leading arm 85 enters the end arc portion 33bc of the cam hole 33b of the master arm 33 so that the leading arm 85 does not swing at the maximum swinging angle, and the master arm 33 swings upstream. The member 51 is rotated to an intermittent feed angle of 60 degrees, the upstream latch arm 71 is swung by the force stored in the torsion coil spring 88, and the leading latch claw 71c is completely engaged with the upstream latch recess 53v. Since the latch claw 81c of the downstream latch arm 81 swinging integrally is released from the downstream latch recess 63v of the downstream rotation member 61, the operation stored in the lost motion spring 60 of the lost motion mechanism 50 is released. The force acts on the downstream side rotation member 61 whose latch is released.

Since the latch angle sensor 95 detects the swing of the downstream latch arm 81 and the multi-plate friction clutch 3 is disconnected based on this detection signal to reduce the resistance in switching the dog clutch of the gear transmission mechanism 10, the lost motion The downstream rotating member 61 smoothly rotates by the operation force stored in the lost motion spring 60 of the mechanism 50, and the downstream rotating member 61 rotates 60 degrees at a stroke, that is, integrated with the downstream rotating member 61. The shift drum 21 is rotated 60 degrees to complete the change of the gear position.
FIG. 12 shows a state where the shift stage has been switched.

Here, when the depression of the shift pedal 30 (shift operation input) is stopped, the master arm 33 swings clockwise together with the shift spindle 31 and the shift pedal 30 by the spring force of the return spring 34 and returns to the neutral position.
FIG. 13 shows this state.
At this time, the driven projection 38b slidably fitted in the drive hole 33c of the master arm 33 is guided and the shift input member 38 rotates in the clockwise direction, but the pole ratchet mechanism 40 is rotated in the clockwise direction of the shift input member 38. For this rotation, the upstream rotation member 51 of the pole 41 is not engaged with the inner peripheral recess 51bh, and the upstream rotation member 51 does not rotate and maintains the previous state.

  Since the master arm 33 returns to the neutral position, the driven pin 86 at the tip of the leading arm 85 returns to the center of the central arc portion 33ba of the cam hole 33b of the master arm 33, and the leading arm 85 swings counterclockwise. At the same time, the upstream latch arm 71 and the downstream latch arm 81 are also integrally pivoted counterclockwise via the torsion coil spring 88, and the latch pawl 71c of the upstream latch arm 71 is upstream of the upstream rotating member 51. The latch pawl 81c of the downstream latch arm 81 engages with the downstream latch recess 63v of the downstream rotation member 61 and restrains the rotation of the downstream rotation member 61 so that the speed change is complete. To finish.

  In the above example, the master arm 33 swings counterclockwise. However, when the master arm 33 swings clockwise, the swing direction and the rotation direction are reversed, Operates and shifts up and down in the same way.

  The present shift shift device 20 has a necessary shift operation input, and the state shown in FIG. 11, that is, the upstream side rotation member 51 rotates to about 50 degrees, and the latch pawl 71c of the upstream side latch arm 71 latches on the upstream side latch. Even if the shift pedal 30 is stopped and the shift operation input is stopped, the latching surface formed at an acute angle with respect to the bottom surface of the upstream latch recess 53v when the latching surface of the recess 53v is engaged. The latching claw 71c is hooked and is not easily released from the bent portion of the upstream latch arm 71, and the upstream pivoting member 51 is kept rotating and stored in the lost motion spring 60. The operation force thus maintained is maintained, and the latch pawl 81c is latched on the latching surface having an obtuse angle with respect to the bottom surface of the downstream latch recess 63v of the downstream rotating member. The latching surface is slippery and the downstream latch recess 63v Exit, the downstream latch arm 81 swings in the clockwise direction, the swing of the downstream latch arm 81 latch angle sensor 95 detects.

  Therefore, since the multi-plate friction clutch 3 is disconnected based on the detection signal of the latch angle sensor 95, the resistance in switching the dog clutch of the gear transmission mechanism 10 is reduced and stored in the lost motion spring 60 of the lost motion mechanism 50. The downstream side rotation member 61 is smoothly rotated together with the shift drum 21 by the operation force, and the shift stage is switched.

  As described above, the present shift shift device 20 is provided with the required rotation of the upstream rotation member 51 of the lost motion mechanism 50 that is rotated from the shift spindle 31 via the intermittent feed mechanism 32 by a shift operation input by depressing the shift pedal 30. Since the upstream side latch mechanism 70 that holds the position is provided, if there is a necessary shift operation input and the required rotation position of the upstream side rotation member 51 of the lost motion mechanism 50 is held, the lost motion mechanism 50 The operating force can be stored and maintained in the lost motion spring 60. Even if the shifting operation input is stopped and the shift spindle 31 is returned before the shifting of the shift stage is completed, the shifting operation input is performed by the force stored and maintained in the lost motion mechanism 50. The shift drum 21 can be rotated without being continued, and the shift can be executed reliably, so that the operability can be improved.

  By providing the downstream latch mechanism 80, the shifting operation force can be reliably stored in the lost motion spring 60 of the lost motion mechanism 50, and when the latch on the downstream latch mechanism 80 is released in a timely manner, it is stored enough. The shift drum 21 can be reliably rotated by the applied force, and the shift stage can be switched reliably.

  The upstream rotating member 51 of the lost motion mechanism 50 has a stopper piece 55 protruding radially from the position between the upstream detent recesses 52v and 52v corresponding to the first speed and the sixth speed on the upstream flower cam 52, respectively. Two stopper pins 59, 59 project from both sides of the right side surface of the guide plate 35 across the roller 58 at the tip of the upstream detent arm 57, and the stopper piece 55 comes into contact with the stopper pins 59, 59. Since the upstream side rotation member 51 is configured with a stopper mechanism whose rotation is restricted within a rotation angle range corresponding to the first speed to the sixth speed, when the rotation of the upstream side rotation member 51 is restricted The shift input member 38 via the pole ratchet mechanism 40 is also restricted from turning in the same direction, and the master arm 33 is also restricted from turning in the same direction, so the depression of the shift pedal 30 in the same direction is also restricted. Is done.

  Therefore, even if the operator attempts to perform a shift operation of the first speed (minimum shift speed) or less and the sixth speed (maximum shift speed) or more with the shift pedal 30, the current shift speed cannot be operated. It can be easily detected.

DESCRIPTION OF SYMBOLS 1 ... Engine case, 2 ... Shift chamber, 3 ... Multi-plate friction clutch, 4 ... Primary gear train, 5 ... Torque damper, 6 ... Push rod, 7 ... Release member, 8 ... Slave hydraulic cylinder,
10 ... Gear transmission mechanism, 11 ... Main shaft, 12 ... Counter shaft, 13,14 ... Bearing, 15 ... Drive sprocket, 16 ... Chain,
20 ... shifting device, 21 ... shift drum, 22,23 ... shift fork shaft, 24,25,26 ... shift fork, 27 ... bearing,
30 ... Shift pedal, 31 ... Shift spindle, 32 ... Intermittent feed mechanism, 33 ... Master arm, 33b ... Cam hole, 33c ... Drive hole, 33d ..., 34 ... Return spring, 35 ... Guide plate, 36 ... Cylindrical pin, 37 ... shift drum shaft, 38 ... shift input member, 39 ... annular sliding member, 40 ... pole ratchet mechanism, 41 ... pole, 42 ... spring,
50 ... Lost motion mechanism, 51 ... Upstream rotating member, 51b ... Large diameter cylindrical portion, 51s ... Small diameter cylindrical portion, 52 ... Upstream flower cam, 52v ... Upstream detent recess, 53 ... Upstream latch flange, 53v ... Upstream latch recess, 54 ... Locking pin, 55 ... Stopper piece, 56 ... Upstream detent mechanism, 57 ... Upstream detent arm, 58 ... Roller, 59 ... Stopper pin, 60 ... Lost motion spring, 61 ... Downstream side Rotating member, 62 ... downstream flower cam, 62v ... downstream detent recess, 63 ... downstream latch flange, 63v ... downstream latch recess, 64 ... locking pin, 66 ... downstream detent mechanism, 67 ... downstream Detent arm, 68 ... Laura,
70 ... Upstream latch mechanism, 71 ... Upstream latch arm, 71c ... Latch claw, 72 ... Lock pin, 75 ... Oscillation center proximal end, 76 ... Latch arm shaft, 77 ... C-type retaining ring,
80 ... downstream latch mechanism, 81 ... downstream latch arm, 81c ... latch claw,
85 ... leading arm, 86 ... driven pin, 87 ... locking pin, 88 ... torsion coil spring,
90 ... latching function switching mechanism, 91 ... electromagnetic solenoid, 92 ... compression coil spring,
95 ... Latch angle sensor.

Claims (3)

In the shift shift device that transmits the rotation of the shift spindle (31) by the shift operation input to the rotation of the shift drum (21) via the intermittent feed mechanism (32) and the lost motion mechanism (50) to perform a shift,
An upstream latch mechanism (70) that holds a required rotation position of the upstream rotation member (51) of the lost motion mechanism (50) rotated through the intermittent feed mechanism (32) by a shift operation input ;
A downstream latch mechanism (80) for latching and regulating the rotation of the downstream rotation member (61) integral with the shift drum (21) on the downstream side of the lost motion mechanism (50) ,
The upstream latch mechanism (70) provided on the upstream side of the lost motion mechanism (50) is formed with a latch recess (53v) corresponding to each shift stage on the outer periphery of the upstream rotation member (51), The swinging upstream latch arm (71) hooks the latch pawl (71c) at the tip to the latch recess (53v),
The downstream latch mechanism (80) has a latch recess (63v) corresponding to each gear position on the outer periphery of the downstream rotation member (61), and a swinging downstream latch arm (81) at the tip. Hook the latch claw (81c) to the latch recess (63v),
The upstream latch arm (71) and the downstream latch arm (81) have a common swing center base end (75) and are pivotally supported by a common latch arm shaft (76) as a unit. A shift shift device characterized by being provided . The common swing center base end (75) is moved in the axial direction by the actuator (91), and the latch claws (71c, 81c) of the upstream latch arm (71) and the downstream latch arm (81) The shift shift device according to claim 1 , further comprising a latching function switching mechanism that disables latching with the corresponding latch recess (53v, 63v). The upstream rotating member (51) of the lost motion mechanism (50) is provided with a stopper mechanism (59) that prohibits the rotation from the minimum gear to the lower gear and the rotation from the maximum gear to the upper gear. The shift shift device according to claim 1 or 2 , characterized in that.

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