JP2627448B2 - Reverse shift method for vehicle gear transmission and vehicle gear transmission - Google Patents

Description

Description of the Invention A. Object of the Invention (1) Field of Industrial Application The present invention relates to a reverse shift method and a vehicle gear transmission for a vehicle gear transmission, and more particularly, to a reverse gear system which is always meshed. The present invention relates to a reverse gear shift method for a vehicle gear transmission and a vehicle gear transmission.

(2) Prior Art Conventionally, in a reverse mechanism for transmitting a driving force of a main shaft of a gear transmission to a counter shaft by reversing the driving force, the main reverse gear and the counter reverse gear are relatively rotatably supported by the main shaft and the counter shaft. At the same time, the reverse idle gear supported on the reverse idle shaft is always meshed with the main reverse gear and the counter reverse gear, and the main reverse gear and the counter reverse gear are respectively coupled to the main shaft and the counter shaft via the sleeve during the reverse shift. A so-called constant-meshing type reverse mechanism is known.

The reverse mechanism is a so-called selective sliding type reverse mechanism in which a reverse idle gear is slid in the axial direction to mesh with a main reverse gear fixed to the main shaft and a counter reverse gear fixed to the counter shaft. It has the following features.

(A) Since the reverse gear train does not rotate at the time of forward movement and at the time of neutral, an increase in the inertia mass of the gear transmission is prevented. As a result, the load on the first- to fifth-speed synchronization mechanisms is reduced.

(B) Since the reverse gear train does not rotate during forward movement and neutral, unnecessary stirring of oil by the reverse gear train is eliminated. This prevents an increase in load due to oil agitation and an increase in oil temperature.

(C) Since the reverse gear train does not rotate at the time of forward movement and at the time of neutral, generation of rattle noise (rattling noise) from the reverse gear train can be prevented.

(D) The helical gear can be employed because the reverse gear series is always meshed, and as a result, the gear noise during reverse running is reduced.

(3) Problems to be Solved by the Invention However, even in the above-described constant-meshing type reverse mechanism, the fact that the flipping sound when the sleeve and the gear mesh with each other due to the reverse shift is not eliminated is different from the selective sliding type reverse mechanism. Absent.

Therefore, it is conceivable to interpose a synchronization mechanism between the main reverse sleeve and the main reverse gear,
Even in this case, when the reverse gear train rotates via the synchronizing mechanism during the reverse shift, a biting sound is generated when the counter reverse sleeve meshes with the counter shaft side, and the shift feeling is deteriorated.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and in a constantly meshing reverse mechanism in which a synchronization mechanism is disposed between a main reverse sleeve and a main reverse gear, the counter reverse sleeve and the counter shaft can be smoothly connected. Accordingly, it is an object to prevent the generation of a biting sound and improve the shift feeling.

B. Configuration of the Invention (1) Means for Solving the Problems In order to achieve the above object, the invention described in claim 1 is a main reverse gear rotatably supported on a main shaft as a drive shaft, and a driven gear. It has a counter reverse gear that is rotatably supported on a counter shaft as a shaft, a reverse gear series including a reverse idle gear that always meshes with the two reverse gears, and a main reverse sleeve that can connect the main reverse gear and the main shaft. A reverse shift method for a vehicle gear transmission including a synchronous coupling mechanism, and a counter reverse sleeve capable of coupling the counter reverse gear and the counter shaft, wherein the counter reverse gear and the counter shaft are connected via the counter reverse sleeve. After starting the coupling, there is a time delay The first feature is that the synchronous action by the synchronous coupling mechanism is started to couple the main reverse gear and the main shaft via the main reverse sleeve.

According to a second aspect of the present invention, there is provided a vehicular gear transmission directly used for performing a reverse shift method in the vehicular gear transmission according to the first aspect, wherein the vehicular gear transmission is rotatable relative to a main shaft as a drive shaft. A reverse gear train comprising a supported main reverse gear, a counter reverse gear rotatably supported on a counter shaft as a driven shaft, and a reverse idle gear constantly meshing with the two reverse gears, and synchronizes the main reverse gear with the main shaft. A main reverse sleeve capable of being coupled via a coupling mechanism, a counter reverse sleeve capable of coupling the counter reverse gear and the countershaft without a synchronous coupling mechanism, and an intermediate portion pivotally supported by a pivot to be pivotally supported. River that drives the main and counter reverse sleeves A shift arm, wherein the synchronous coupling mechanism contacts the first dog tooth formed on the main reverse sleeve, the second dog tooth formed on the main reverse gear, and the main reverse gear via a tapered cone surface. And a third dog tooth formed between the first and second dog teeth formed on the reverse blocking ring that can be contacted, wherein the first dog tooth is in contact with the third dog tooth. The second dog is configured to generate the time delay by the time required for the first dog tooth to move the distance and mesh with the third dog tooth. Features.

According to a third aspect of the present invention, there is provided a vehicular gear transmission directly used for performing a reverse shift method in the vehicular gear transmission according to the first aspect, wherein the vehicular gear transmission is rotatable relative to a main shaft as a drive shaft. A reverse gear train comprising a supported main reverse gear, a counter reverse gear rotatably supported on a counter shaft as a driven shaft, and a reverse idle gear constantly meshing with the two reverse gears, and synchronizes the main reverse gear with the main shaft. A main reverse sleeve capable of being coupled via a coupling mechanism, a counter reverse sleeve capable of coupling the counter reverse gear and the counter shaft without a synchronous coupling mechanism, and a reverse in which an intermediate portion is pivotally supported by a pivot. And a shift arm, wherein the reverse shift arm is A short arm extending in one direction to drive the main reverse sleeve, and a long arm extending from the pivot in the other direction and driving the counter reverse sleeve longer than the short arm. The third feature is that the time delay is generated based on the stroke difference at the tip of the.

(2) Operation According to the first feature described above, the reverse gear series is in the non-rotation state at the start of the reverse shift operation, and the counter shaft is in the non-rotation state because the vehicle is stopped. By the reverse shift operation, the connection between the counter reverse gear and the counter shaft is first started via the counter reverse sleeve, but as described above, since the counter reverse gear and the counter shaft are both in the stopped state, the connection is smoothly performed. Will be Subsequently, with a time delay, the synchronizing operation by the synchronizing coupling mechanism is started, and the main reverse gear and the main shaft are coupled via the main reverse sleeve. At this time, the main shaft is in a rotating state due to inertia after the clutch is disengaged, while the main reverse gear is in a non-rotating state, but the coupling is smoothly performed by the synchronizing action. In this way, by connecting the counter reverse gear and the counter shaft via the counter reverse sleeve and then connecting the main reverse gear and the main shaft via the main reverse sleeve, the gear noise during the reverse shift is eliminated and the shift is performed. Feeling is improved.

According to the second feature of the present invention, when the main reverse sleeve is driven by the reverse shift arm so as to couple the main reverse gear to the main shaft by the synchronous coupling mechanism, the first dog tooth formed on the main reverse sleeve is changed. The configuration of the short teeth increases the time required for the first dog teeth to move and mesh with the third dog teeth formed in the reverse blocking, and as a result,
It is possible to cause a time delay in starting the synchronization action by the synchronization coupling mechanism. As a result, the connection of the counter reverse gear and the counter shaft by the counter reverse sleeve is performed before the connection of the main reverse gear and the main shaft by the main reverse sleeve, and occurrence of gear noise is prevented.

Further, according to the third aspect of the present invention, since the shorter arm of the short arm and the long arm of the reverse shift arm drives the main reverse sleeve of the synchronous coupling mechanism, the start of the synchronization action by the synchronous coupling mechanism. Can cause a time delay. As a result, the connection of the counter reverse gear and the counter shaft by the counter reverse sleeve is performed before the connection of the main reverse gear and the main shaft by the main reverse sleeve, and occurrence of gear noise is prevented.

(3) Example Hereinafter, an example of the present invention will be described with reference to the drawings.

1 to 4 show a first embodiment of the present invention.
FIG. 1 is a sectional view of a main part of the gear transmission, FIG. 2 is an enlarged view of a main part of FIG. 1 showing details of a synchronizing mechanism, FIG. 3 is a perspective view of the transmission mechanism, and FIG. It is explanatory drawing of an operation | movement.

As shown in FIG. 1, a casing 1 of the gear transmission is provided.
Inside, an input side main shaft 3 supported via a ball bearing 2 and an output side counter shaft 6 supported via a ball bearing 4 and a needle bearing 5 are arranged in parallel with each other.

A main reverse gear 9 is rotatably and coaxially supported relative to the main shaft 3 via a ball bearing 7 and a needle bearing 8 at a tip of the main shaft 3, and a counter reverse gear is provided at a tip of the counter shaft 6. 10 is rotatably supported via needle bearings 11 and 12. A reverse idle gear 17 fixed to the end of the casing 1 with bolts 13 is supported via needle bearings 15 and 16 on a reverse idle shaft 14. The reverse idle gear 17 is composed of the main reverse gear 9 and the counter reverse gear 9. 10 meshed. The reverse gear series Gr including the main reverse gear 9, the reverse idle gear 17, and the counter reverse gear 10 is separated from the main shaft 3 and the counter shaft 6 except during the reverse shift. The stopped state is maintained by the frictional force received from the spring washer 18 mounted between the end face and the casing 1.

On the other hand, a main fifth speed gear 20 rotatably supported on the main shaft 3 via a needle bearing 19, and a counter fifth speed gear 21 constantly meshed with the main fifth speed gear 20 and spline-coupled to the counter shaft 6 from a fifth speed gear 21 gear series G ₅ is composed.

Main reverse gear 9 of main shaft 3 and main 5
The main reverse gear 9 and the main 5
A synchronous coupling mechanism 22 for selectively coupling the speed gear 20 to the main shaft 3 is provided. The synchronous coupling mechanism 22 includes a main reverse sleeve 25 supported on the outer periphery of a synchronizer hub 23 spline-coupled to the main shaft 3 and sliding in the axial direction with a main reverse fork 24. When the main reverse gear 9 is engaged with the dog teeth 9a of the main reverse gear 9 so as to be relatively non-rotatable with the main shaft 3, the main reverse sleeve 25 slides leftward to move the main reverse gear 9 in the main direction. When the dog gear 20a of the fifth speed gear 20 is engaged, the main fifth speed gear 20 and the main shaft 3 are connected to each other so that they cannot rotate relative to each other.

On the other hand, a counter reverse sleeve 26 is spline-coupled to the outer periphery of the counter reverse gear 10 so as to be slidable in the axial direction. The counter reverse sleeve 26 is slid leftward in the figure by a counter By engaging the dog teeth 21 a of the gear 21, the counter reverse gear 10 is coupled to the counter shaft 6 via the counter fifth-speed gear 21 so as to be relatively non-rotatable.

Next, the synchronous coupling mechanism 22 will be described in detail with reference to FIG. The synchronous coupling mechanism 22 is provided with a synchronizer hub 23 spline-coupled to the main shaft 3, a main reverse sleeve 25 axially slidably coupled to the outer periphery of the synchronizer hub 23, and between the synchronizer hub 23 and the main reverse gear 9. Reverse blocking ring 28, synchronizer hub 23 and main 5th gear 20
It comprises a fifth-speed blocking ring 29 disposed therebetween, and a synchronizer hub 23 and synchronizer springs 30, 31 disposed between the blocking rings 28, 29. A dog tooth 28a meshable with a spline tooth formed on the inner peripheral surface of the main reverse sleeve 25 is formed on the outer periphery of the reverse blocking ring 28, and a tapered cone surface formed on the main reverse gear 9 is formed on the inner periphery thereof. A taper cone surface 28b engageable with 9b is formed. The blocking ring 29 for the fifth speed is also the same as the blocking ring 28 for the reverse, and the main reverse sleeve.
Dog teeth that can mesh with spline teeth formed on the inner peripheral surface of 25
29a and a tapered cone surface 29b engageable with a tapered cone surface 20b formed on the main fifth speed gear 20.

FIGS. 4A to 4C show long teeth 25a and short teeth 25b of spline teeth of a main reverse sleeve 25, dog teeth 28a of a reverse blocking ring 28, and dog teeth 29a of a 5-speed blocking ring 29. , The dog teeth 9a of the main reverse gear 9 and the dog teeth 20a of the main fifth speed gear 20 are shown in an expanded state.

As apparent from FIG. 4 (a), of the spline teeth formed on the inner periphery of the main reverse sleeve 25, a total of six spline teeth separated by 120 ° in the circumferential direction, that is, Dog teeth 28a of the blocking ring 28 for
The short spline teeth 25b are retracted on the side, and all other spline teeth are long teeth 25a extending over the entire width of the main reverse sleeve 25. Therefore, the tips of the long teeth 25a and the short teeth 25b of the main reverse sleeve 25 are linearly aligned on the dog teeth 29a side of the fifth speed blocking ring 29, but the dog teeth of the reverse blocking ring 28
A step A is formed on the 28a side.

The dog teeth 29a of the fifth speed blocking ring 29 are formed over the entire circumference of the fifth speed blocking ring 29 so as to correspond to the long teeth 25a and the short teeth 25b, respectively. On the other hand, the dog teeth 28a of the reverse blocking ring 28 are formed two at a position 120 ° apart on the outer periphery of the reverse blocking ring 28 so as to correspond to only the short teeth 25b, that is, a total of six dog teeth 28a. The distance B between the tips of the long teeth 25a and the short teeth 25b of the main reverse sleeve 25 and the dog teeth 29a of the fifth speed blocking ring 29 is a normal value, but the short teeth 25b and the reverse blocking ring 28
The distance C between the dog teeth 28a is set to be greater than the distance B. Therefore, a slightly extra moving distance than usual is required for the main reverse sleeve 25 to slide in the direction of arrow a to start the synchronizing action.

As shown in FIG. 3, a main fork shaft 32 disposed in parallel with the main shaft 3 supports a main reverse fork 24 for driving a main reverse sleeve 25 of the synchronous coupling mechanism 22. A counter reverse fork 27 for driving the counter reverse sleeve 26 is supported on a counter fork shaft 33 disposed in parallel with the counter 8. A reverse shift arm 36 is pivotally supported by a bracket 34 fixed to the casing 1 via a pivot 35. A hook-shaped through hole 37a formed at the tip of an arm 37 extending to one end is implanted in the main reverse fork 24. The tip of the arm 37 having the same length as the arm 37 extending in the other direction is engaged with the groove 40 formed in the counter reverse fork 27 while being engaged with the pin 38 provided.

Next, the operation of the embodiment of the present invention having the above-described configuration will be described.

When the shift rod (not shown) is operated to the reverse position, the main fork shaft 32 and the main reverse fork 24 are driven in the direction of arrow b in FIG. 3, and the main reverse sleeve 25 engaged with the main reverse fork 24 is moved in FIG. To the right in the main reverse gear 9
Approach. The movement of the main reverse fork 24 swings the reverse shift arm 36 around the pivot 35 via the pin 38 and the through hole 37a of the arm 37, and the swing of the reverse shift arm 36 engages the tip of the arm 39. The counter reverse fork 27 is driven through the groove 40 in the direction of arrow c. As a result, the counter reverse sleeve 26 engaged with the counter reverse fork 27 slides leftward in FIG. In this manner, the main reverse fork 24 and the counter reverse fork 27 interlocked via the two equal-length arms 37 and 39 of the reverse shift arm 36 cause the main reverse sleeve 25 and the counter reverse sleeve 26 to reverse at the same speed. The main reverse gear 9 and the counter reverse gear 10 are connected to the main shaft 3 and the counter shaft 6, respectively. At this time, the synchronous action of the main reverse gear 9 and the main shaft 3 by the synchronous coupling mechanism 22 is started with a slight time delay from the start of the coupling of the counter reverse gear 10 and the counter shaft 6 by the counter reverse sleeve 26.

Next, the reason why the above-mentioned time delay occurs with respect to the start timing of the synchronous action of the synchronous coupling mechanism 22 will be described with reference to FIGS. 2 and 4. FIG.

In FIG. 2, when the main reverse sleeve 25 of the synchronization mechanism 22 slides toward the main reverse gear 9,
The long teeth 25a of the main reverse sleeve 25 pass over the synchronizer spring 30 without contacting it. Further, when the main reverse spring 25 slides, protrusions 25c formed on both sides of the short teeth 25b so as to face inward contact the synchronizer spring 30, and the synchronizer spring
The blocking ring 28 for reverse is pressed via 30 to bring its tapered cone surface 28b into contact with the tapered cone surface 9b of the main reverse gear 9, and a frictional force is generated between the two tapered cone surfaces 28b, 9b to cause the main reverse sleeve 25, A synchronizing action between the shaft 3 and the main reverse gear 9 is started. Due to this frictional force, the reverse blocking ring 28 slightly rotates, so that the chamfer of the dog teeth 28a takes a position to be engaged with the chamfer of the short teeth 25b of the main reverse sleeve 25, and the main reverse sleeve 25 further slides. When the travel distance reaches C, the dog tooth
The reverse blocking ring 28 is pressed with a strong force by the direct engagement of the chamfer 28a and the chamfer 25b with the short teeth 25b, and a strong frictional force is generated between the tapered cone surface 28b and the tapered cone surface 9b of the main reverse gear 9 to synchronize. The action proceeds rapidly (see FIG. 4 (b)). By this synchronizing action, the main shaft 3 is braked to be in the same stopped state as the main reverse gear 9, and the main reverse sleeve 9 is stopped.
When 25 advances further, the long teeth of main reverse sleeve 25
25a meshes with the dog teeth 9a of the main reverse sleeve 9, and the connection between the main reverse sleeve 25 and the main reverse gear 9, that is, the connection between the main shaft 3 and the main reverse gear 9 is completed (see FIG. 4 (c)).

During the operation of the synchronous coupling mechanism 22 described above, the time from the moment when the main reverse sleeve 25 starts sliding to the time when the synchronizing action is started, that is, the main reverse sleeve 25
The time required for the 25 short teeth 25b to come into contact with the synchronizer spring 30 is slightly longer than usual because the protruding portion 25c that comes into contact with the synchronizer spring 30 is provided at the tip of the short teeth 25b. Therefore, even when the main reverse sleeve 25 and the counter reverse sleeve 26 are driven at the same speed, the connection timing of the counter reverse gear 10 is slightly ahead of the start timing of the synchronization operation of the synchronous connection mechanism 22.

By the way, at the start of the reverse shift operation, since the vehicle is in a stopped state, the counter shift 6 and the fifth counter gear 21 are stopped, and the reverse gear Gr is also in a non-rotating state. Accordingly, the connection of the counter reverse gear 10 and the counter fifth speed gear 21 by the counter reverse sleeve 26 starts smoothly without any problem.

Subsequently, with a slight time delay, the synchronizing operation by the synchronizing coupling mechanism 22 is started, and the main reverse gear 9 and the main shaft 3 are coupled via the main reverse sleeve 25. At this time, the main shaft 3 is in a rotating state due to inertia after the clutch is disconnected, while the main reverse gear 9
Is in a non-rotation state, but the connection is smoothly performed by a synchronizing operation performed prior to the connection of the long teeth 25a of the main reverse sleeve 25 and the dog teeth 9a of the main reverse gear 9.

Assuming that the timing of the connection is reversed, the first connection between the main reverse gear 9 and the main shaft 3 is smoothly performed by the synchronization mechanism 22,
Counter reverse sleeve without synchro mechanism because the reverse gear series Gr starts rotating by the above connection
26 counter reverse gear 10 and counter 5th gear 21
When the gears are combined, a gear noise is generated and the shift feeling deteriorates.

Also, if the vehicle accidentally performs a reverse shift operation while traveling forward at a speed higher than a predetermined speed (for example, 10 km / h or more),
Since the countershaft 6 and the counter fifth gear 21 are rotating, relative rotation occurs between the counter shaft 6 and the stopped counter reverse gear 10, and as a result, the counter reverse sleeve 26 having no synchronizing mechanism is moved to the counter 5 speed. Gear 21
Gear 21 is repelled by the dog teeth 21a. This prevents a reverse shift due to an erroneous operation during forward running.

FIG. 5 shows a second embodiment of the present invention. This embodiment is characterized in that the time delay is generated by a transmission mechanism.

That is, in this embodiment, the length of the two arms of the reverse shift arm 36 'is different, and the main reverse fork
Arm 24 'is short arm 37' and counter reverse fork 27
The side arm is a long arm 39 '. The configuration of the synchronous coupling mechanism 22 mounted on the main shaft 3 is slightly different from that of the previous embodiment. All the spline teeth of the main reverse sleeve 25 are formed as long teeth 25a, and the reverse blocking ring 28 is formed. Is provided with dog teeth 28a all around its circumference. Therefore, the synchronous coupling mechanism 22 is configured so that the main reverse gear 9 side and the main fifth speed gear 20 side are symmetrical, and the synchronous coupling mechanism 22 is configured so that the time delay does not occur.

According to this embodiment, the moving speed of the counter reverse fork 27 connected to the long arm 39 'of the reverse shift arm 36' is reduced by the main reverse fork 24 connected to the short arm 37 '.
Than the moving speed of. Accordingly, the start of the connection of the counter reverse gear 10 by the counter reverse sleeve 26 moving at a high speed precedes, and the synchronization operation by the main reverse sleeve 25 moving at a low speed and the subsequent connection with the main reverse gear 9 start with a slight time delay. Is done.

Thus, according to the second embodiment, the same operation and effect as those of the first embodiment can be obtained. Further, the first embodiment and the second embodiment can be combined for the purpose of obtaining the same operation and effect.

C. Effects of the Invention As described above, according to the present invention, after the counter shaft and the counter reverse gear in the non-rotation state are first connected by the counter reverse sleeve by the reverse shift operation, the main shaft in the rotation state with a time delay After the synchronizing action between the main reverse gear in the stopped state and the main shaft is also stopped,
Since the main shaft and the main reverse gear are connected by the main reverse sleeve, the reverse shift can be completed without generating a biting noise.

If the reverse shift operation is performed by mistake while the vehicle is traveling forward, the counter shaft connected to the wheels rotates and a relative rotation occurs between the counter shaft and the stopped counter reverse gear. As a result, the counter reverse sleeve having no synchronous coupling mechanism is repelled and gear noise is generated, thereby preventing a reverse shift due to an erroneous operation during forward running.

[Brief description of the drawings]

1 to 4 show a first embodiment of the present invention. FIG. 1 is a sectional view of a main part of the gear transmission, and FIG. 2 is a main part of FIG. 1 showing details of a synchro mechanism. FIG. 3 is an enlarged view, FIG. 3 is a perspective view of the transmission mechanism, FIG. 4 is an explanatory view of the operation of the synchronization mechanism, and FIG. 5 shows a second embodiment of the present invention. It is a perspective view. 3 ... Main shaft, 6 ... Counter shaft, 9 ...
... Main reverse gear, 9a ... dog teeth (second dog teeth), 9b ... taper cone surface, 10 ... counter reverse gear, 17 ... reverse idle gear, 22 ... synchro mechanism (synchronous coupling mechanism), 25 …… Main reverse sleeve,
25b Short tooth (first dog tooth), 26 Counter reverse sleeve, 28 Reverse blocking ring, 28
a ... dog tooth (third dog tooth), 28b ... taper cone surface, 35 ... pivot, 36 ... reverse shift arm, 36 '...
… Reverse shift arm, 37 ′ …… Short arm, 39 ′ …… Long arm, Gr …… Reverse gear series

Claims (3)

(57) [Claims] 1. A main reverse gear (9) rotatably supported on a main shaft (3) as a drive shaft, a counter reverse gear (10) rotatably supported on a counter shaft (6) as a driven shaft, and A reverse gear series (Gr) comprising a reverse idle gear (17) constantly meshing with the two reverse gears (9, 10); the main reverse gear (9) and a main shaft (3)
And a counter reverse sleeve (26) capable of connecting the counter reverse gear (10) and the counter shaft (6) without a synchronous connection mechanism. ) And a reverse shift method in a vehicle gear transmission comprising: a counter delay sleeve (26), a time delay after starting the connection of the counter reverse gear (10) and the counter shaft (6). The synchronous coupling mechanism (22)
To start the synchronizing action by the main reverse gear (9)
And a main shaft (3) through the main reverse sleeve (25). 2. A vehicular gear transmission directly used for carrying out a reverse shift method in a vehicular gear transmission according to claim 1, wherein the vehicular gear transmission is rotatably supported on a main shaft (3) serving as a drive shaft. A reverse gear (9), a counter reverse gear (10) rotatably supported on a counter shaft (6) as a driven shaft, and a reverse idle gear (17) constantly meshing with the two reverse gears (9, 10). Reverse gear series (Gr), the main reverse gear (9) and the main shaft (3)
And a counter reverse sleeve (26) capable of connecting the counter reverse gear (10) and the counter shaft (6) without a synchronous connection mechanism. ), And a reverse shift arm (36) whose intermediate portion is pivotally supported by a pivot (35) to drive the main reverse sleeve (25) and the counter reverse sleeve (26). The synchronous coupling mechanism (22) includes a first dog tooth (25b) formed on the main reverse sleeve (25), a second dog tooth (9a) formed on the main reverse gear (9), and a main reverse gear ( 9) a third dog formed between the first and second dog teeth (25b, 9a) and formed on a reverse blocking ring (28) that can be contacted via a tapered cone surface (9b, 28b). Tooth (28a) The first dog tooth (25b) is configured as a short tooth having a large distance from the third dog tooth (28a), and the first dog tooth (25b) is Move the distance to the third dog tooth (28a)
The vehicle gear transmission according to claim 1, wherein the time delay is caused by a time required for meshing with the vehicle gear. 3. A vehicular gear transmission directly used for carrying out a reverse shift method in a vehicular gear transmission according to claim 1, wherein the vehicular gear transmission is rotatably supported on a main shaft (3) serving as a drive shaft. A reverse gear (9), a counter reverse gear (10) rotatably supported on a counter shaft (6) as a driven shaft, and a reverse idle gear (17) constantly meshing with the two reverse gears (9, 10). Reverse gear series (Gr), the main reverse gear (9) and the main shaft (3)
And a counter reverse sleeve (26) capable of connecting the counter reverse gear (10) and the counter shaft (6) without a synchronous connection mechanism. ), And a reverse shift arm (36 ') whose intermediate portion is pivotally supported by a pivot (35), wherein the reverse shift arm (36') is unidirectional from the pivot (35). And a short arm (37 ') extending from the pivot (35) in the other direction to drive the counter reverse sleeve (26). A vehicle gear having a long arm (39 '), wherein the time delay is generated based on a stroke difference between the tip of the short arm (37') and the long arm (39 '). transmission.