JP2002227939A - Gear type transmission for off-road traveling vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gear type transmission for an off-road traveling vehicle which achieves miniaturization of dimensions in a transmission shaft axis direction and in a perpendicular direction to the shaft axis direction, and improves assemblability. SOLUTION: A transmission case 11 integrally formed with a crank case 10 of an engine is provided with a speed change input shaft 62, a speed change output shaft 63 and a speed change intermediate shaft which are in parallel with a crank shaft 36. A dog clutch mechanism choosing two stages for forward, neutral and reverse by the movement of a single shift sleeve 70 is arranged in the speed change input shaft 62. The intermediate shaft is equipped with a counter shaft 64 provided with an intermediate gears 73 and 74 for forward meshing with respective gears 67 and 68 for forward of the speed change input shaft 62, and with an idle shaft 65 for reverse provided with an idle gears 77 for reverse meshing with the gear 69 for reverse of the speed change input shaft 62. The counter shaft 64 is placed on the closer side to the crank shaft vertically between the speed change input and output shafts 62 and 63. The idle shaft 65 is placed on the far side to the crank shaft.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission input shaft, a transmission output shaft, and a transmission intermediate shaft arranged in parallel with a crankshaft in a transmission case formed integrally with a crankcase of an engine. The present invention relates to a gear transmission for an off-road vehicle supporting a shaft.

[0002]

2. Description of the Related Art A conventional gear-type transmission for an all-terrain vehicle is:
As a reverse power transmission mechanism, a chain transmission mechanism is interposed between the speed change input shaft and the counter shaft. FIG. 7 shows an example of a conventional structure. In a transmission case 200, a transmission input shaft 202 coupled to a driven shaft 201 of a V-belt type continuously variable transmission, and a counter shaft (intermediate shaft) 203.
And a transmission output shaft 204 provided in parallel with each other. The speed change input shaft 202 is provided with forward high speed and low speed forward gears 205 and 206 and a reverse chain wheel 207. Each of the forward gears 20 is provided on the counter shaft 203.
5 and 206, respectively.
211, an intermediate output gear 213, and a large-diameter reverse chain wheel 212 connected to the reverse chain wheel 207 via a chain 215. Output shaft 20
4 is an output gear 216 meshing with the intermediate output gear 213
And a bevel gear 222 that meshes with the bevel gear 221 of the drive shaft 220.

As shift dog clutch mechanisms, shift sleeves 225 and 22 are provided at two positions on a counter shaft 203.
6, one shift sleeve 225 is composed of a reverse chain wheel 212 and a forward high speed intermediate gear 210.
, And the remaining shift sleeve 226 is disposed next to the forward low-speed intermediate gear 211.

One shift rod 230 is provided and has shift arms (shift forks) 231A and 231B which engage with the shift sleeves 225 and 226.

In the gear type transmission shown in FIG. 7, switching to forward high speed or reverse is performed by moving one shift sleeve 225, and switching to low forward speed is performed by moving the other shift sleeve 226. Do.
The known technical literature is disclosed in Japanese Patent Application Laid-Open No. 62-106162.
There is an official gazette.

Also, without using the above-described chain transmission mechanism, a reverse idle shaft is arranged between the speed change input shaft and the counter shaft and the like, so that the output shaft is reversely rotated by gears to move backward. There is also a gear type transmission having a structure as described above.

[0007]

Problems to be Solved by the Invention (1) As shown in FIG.
In a gear transmission having a chain transmission mechanism for reverse power transmission, it is not necessary to provide an idle shaft for reverse reversal as an intermediate shaft. 215 needs to be formed wider in the direction of the transmission shaft center, so that the size of the transmission case 200 in the direction of the transmission shaft becomes larger, and it takes time to assemble the chain transmission mechanism.

(2) In the chain transmission mechanism, a tensioner may be required in order to prevent the rattling or rattling of the chain 215 due to the use in consideration of the extension of the chain 215 due to use.

(3) In a gear type transmission in which a reverse idle shaft for reverse reversal is added as a transmission intermediate shaft and a chain transmission mechanism is not used, the number of transmission shafts increases by one, so that the transmission case becomes large. However, there is a problem that the structure inside the transmission is complicated.

[0010]

The object of the present invention is to reduce the width of the transmission case in the direction of the transmission shaft axis and to add a reverse idle shaft as a transmission intermediate shaft, despite the fact that the transmission case is perpendicular to the transmission shaft center direction. An object of the present invention is to provide a gear type transmission for an all-terrain vehicle that can be reduced in size and that has a simple configuration and that does not require much assembly work.

[0011]

According to a first aspect of the present invention, there is provided a transmission case integrally formed with a crankcase of an engine, a transmission input shaft disposed in parallel with the crankshaft, and a transmission input shaft arranged in parallel with the crankshaft. In a gear transmission of an off-road vehicle that supports an output shaft and an intermediate shaft for shifting, a dog clutch mechanism that switches between two forward stages, neutral, and reverse by moving a single shift sleeve to an input shaft for shifting. And a countershaft with a forward intermediate gear meshing with each forward gear of the speed change input shaft, and a reverse with a reverse idle gear meshing with the reverse gear of the speed change input shaft as the speed change intermediate shaft. A transmission input shaft and a transmission output shaft are arranged vertically above and below the transmission case, and between the transmission input shaft and the transmission output shaft, Input shaft and speed change output Side counter shaft is arranged closer to the crank shaft with respect to a line connecting the axis, it is characterized in that is disposed a reverse idle shaft on the far side from the crankshaft.

As a result, the size of the transmission case in the direction of the transmission shaft center can be made smaller than that of the chain type, while maintaining a structure capable of withstanding a large transmission torque. In particular, since the uneven terrain vehicle is of a riding type, if the size of the transmission case in the direction of the transmission shaft becomes compact, a large space for the rider's foot can be secured and the riding comfort is improved.

A dog clutch mechanism in which a speed change input shaft and a speed change output shaft are vertically spaced from each other, and a single shift sleeve is moved on the speed change input shaft to switch between forward two-stage, neutral and reverse. By disposing the intermediate shaft, a large space is provided for the intermediate shaft, and the counter shaft is disposed on the crankshaft side (front side), and the idle shaft is disposed on the rear side. The space in the crankcase (in the transmission case) between the transmission input shafts can be efficiently used, and the transmission has a simple configuration despite the additional intermediate shaft compared to the chain type. The dimensions of the case in the direction perpendicular to the center axis of the transmission shaft, particularly the dimensions in the front-rear direction, can be compacted.

According to a second aspect of the present invention, in the gear transmission for an uneven terrain vehicle according to the first aspect, the reverse idle gear is a first reverse idle gear that meshes with the reverse gear of the speed change input shaft. And a second reverse idle gear meshing with the intermediate output gear on the counter shaft.
The reverse idle gear is characterized in that it is arranged close to one end side in the axial direction of the reverse idle shaft.

As a result, the reduction ratio can be increased without using a large-diameter reverse reduction gear or a large-diameter chain wheel, and the size of the transmission case in the direction perpendicular to the transmission shaft center can be reduced. Can be. In addition, by disposing the two reverse idle gears at one end in the direction of the axis of the transmission shaft, the two reverse idle gears are located near the support point of the bearing. The influence is small, and the meshing accuracy of the reverse idle gear can be maintained. Further, the assemblability of the reverse idle gear is also improved.

According to a third aspect of the present invention, in the gear transmission for an uneven terrain vehicle according to the second aspect, the reverse idle shaft is supported at both end walls of the transmission case in the direction of the reverse idle shaft center. In addition, a portion opposite to the side on which the first and second reverse idle gears are disposed is formed to have a small diameter.

Thus, for example, the outer peripheral end of the forward low-speed intermediate gear having the maximum outer diameter on the counter shaft is disposed close to the outer peripheral surface of the small-diameter portion, so that the center shaft between the counter shaft and the reverse idle shaft is disposed. The distance can be reduced, and the width of the transmission case in the front-rear direction and the like can be reduced.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is a plan view of a four-wheeled vehicle on a rough terrain to which the present invention is applied. .

The rough terrain vehicle has a pair of left and right front wheels 1 and a pair of right and left rear wheels 2, and has an engine 3 mounted between the front and rear wheels 1 and 2; It has. A bar-shaped steering handle 5 is provided at the front of the vehicle body, and a riding type seat 6 is provided at the rear. The grip of the steering handle 5 is provided with a brake lever 8 and the like.

The crankcase 10 of the engine 3 extends rearward and integrally has a transmission case 11 at the rear end.
In the transmission case 11, a gear type transmission 13 is incorporated. On the right side surface of the crankcase 10, a V-belt type continuously variable transmission 15 located on the power upstream side of the gear type transmission 13 is arranged.

A front and rear drive shaft 17 is disposed below the transmission case 11, and a front and rear end of the drive shaft 17 have a front wheel propeller shaft 18 and a rear wheel propeller shaft, respectively. The front end of the front wheel propeller shaft 18 is connected to a gear mechanism in a front wheel reduction gear case 21, and the rear end of the rear wheel propeller shaft 12 is connected to a gear mechanism in a rear wheel reduction gear case 22. It is connected to.

FIG. 2 is a right side view of FIG.
The V-belt type continuously variable transmission 15 includes a front drive pulley 26, a rear driven pulley 28, and a V wound around the pulleys 26 and 28. It comprises a belt 29 and is covered by a belt converter cover 30.

A shift operation lever 32 is disposed below the right end of the handle 5, and the shift operation lever 32 is
The transmission case 11 is interlockingly connected to an outer chain lever 35 disposed at an upper end portion of the transmission case 11 via a connection rod 33.

[V-belt type continuously variable transmission] FIG. 4 is a cross-sectional view taken along a cut plane passing through the crankshaft axis O0. The drive shaft 25 of the drive pulley 26 is provided on the same shaft center at the right end of the crankshaft 36. The generator 38 and the recoil starter 39 are disposed on the left side of the crankshaft 36. The drive pulley 26 includes a left fixed sheave 41,
The movable sheave 42 is opposed to the fixed sheave 41 from the right side. The fixed sheave 41 is fixed to the drive shaft 25 so that it cannot rotate and cannot move in the axial direction. The movable sheave 42 is fixed to the drive shaft 25 in the rotational direction.
4 so as to be integrally rotatable and fitted to be movable in the axial direction.

On the back side (right side) of the movable sheave 42, a driving pulley thrust generating mechanism including the spider 44, a plurality of fly weights 45, a pressure adjusting spring 46, a support plate 47 and the like is provided. The fly weight 45 is rotatably supported by a plurality of pins 48 provided on the back surface of the movable sheave 42, and expands to the right due to centrifugal force as the rotation speed of the drive shaft 25 increases. Has become. A connecting arm 49 extending rightward through the spider 44 is formed on the rear surface of the movable sheave 42, and a support board 47 is connected to a right edge of the connecting arm 49. The support board 47 is fitted to the drive shaft 25 so as to be movable in the axial direction, and a bearing 50 is fitted to an inner peripheral end of the support board 47.
An annular seat 51 with which the contact is made is fitted.

The spider 44 is provided on the right side of the movable sheave 42 and is screwed to the drive shaft 25, and has a pressure receiving roller 52 with which the flyweights 45 come into contact. The pressure adjusting spring 46 is contracted between the spider 44 and the support board 47, and biases the support board 47 rightward to indirectly attach the movable sheave 42 rightward via the connecting arm 49. I'm going. That is, the driving pulley 2
No. 6 urges the sheaves 41 and 42 in the opening direction.
When the flyweight 45 expands due to an increase in the engine speed, the movable sheave 42 moves to the left together with the support plate 47 against the pressure adjusting spring 46 due to the reaction force of the pressure receiving roller 52, and between the sheaves 41, 42. Nips the V-belt 29.

The driven pulley 28 includes a right fixed sheave 54 and a left movable sheave 55 as shown in FIG. The fixed sheave 54 is fixed to the cylindrical cam shaft 56 fixed to the driven shaft 27 so as not to be movable in the axial direction and to be rotatable. The cam shaft 56 has a spiral cam guide groove 57.
Are formed. The movable sheave 55 has a sleeve 58 fixed to the inner peripheral end thereof fitted to the camshaft 56 so as to be movable and rotatable in the axial direction, and is urged toward the fixed sheave by a pressure adjusting spring 59. The cam roller 60 supported by the sleeve 58 is slidably engaged with the cam guide groove 57.

That is, when the rotational torque from the V-belt 29 increases and the movable sheave 55 is twisted forward in the rotational direction, the movable sheave 55 is pushed toward the fixed sheave by the cam action of the cam roller 60 and the cam guide groove 57. , Increase the clamping pressure.

[Gear-Type Transmission and Shift Mechanism] FIG. 6 is a left side view in vertical section showing an arrangement of a transmission shaft in a transmission case 11 integrated with the crankcase 10. A transmission input shaft 62 is disposed to face left and right, a transmission output shaft 63 is disposed near the lower end in parallel with the input shaft 62, and an input shaft center is disposed between the input shaft 62 and the output shaft 63. The counter shaft 64 is arranged in parallel with the input shaft 62 on the front side (crankshaft arrangement side) of the line connecting O1 and the output shaft center O4, and the reverse idle shaft 65 is arranged on the rear side in parallel with the input shaft 62. I have. The counter shaft 64 and the reverse idle shaft 65 are arranged at substantially the same height. Further, a single shift rod 72 is disposed at a position obliquely above and behind the input shaft 62 in parallel with the input shaft 62. By arranging the counter shaft 64 having the largest forward low-speed intermediate gear 74 having the largest diameter as described above on the front side where there is room in space and the reverse idle shaft 65 on the rear side, the transmission case 11 There is no need to extend the wall backward.
The drive shaft 17 is disposed at substantially the same height as the output shaft 63.

FIG. 5 is a sectional development view (VV sectional development view in FIG. 6) of the inside of the transmission case 11 cut along a plane passing through each of the transmission shaft cores O1, O2, O3 and O4. The axis 62 is
The driven pulley 28 is formed integrally with the driven shaft 27. Input shaft 62, counter shaft 64 and reverse idle shaft 6
5 is supported on the left and right side walls of the transmission case 11 via bearings, but the output shaft 63 is formed shorter than the shafts 62, 64, and 65 for each of the transmissions. It is supported by a shaft holder 66 fixed therein, via a pair of left and right bearings 61. The drive shaft 17 is disposed on the right side of the output shaft 63.

At the right end of the input shaft 62, a forward high-speed gear 67 and a forward low-speed gear 68 are arranged in parallel in an axially adjacent state, and at the left end, a reverse gear 69 is arranged.
A single shift sleeve 70 that constitutes a dog dog clutch mechanism for shifting between two steps forward, neutral and reverse is spline-fitted to the central portion so as to be movable in the axial direction.

The reverse gear 69 has a dog claw 69a on the right end surface.
And is rotatably fitted to the input shaft 62 via a needle bearing. The forward low-speed gear 68 has a dog claw 68a on the left end edge of a boss portion extending leftward.
The input shaft 62 is rotatably fitted via a needle bearing. The forward high speed gear 67 has an inward dog claw 67a at the left end of the arm portion extending leftward, and is rotatably fitted to the outer periphery of the boss portion of the forward low speed gear 68 via a needle bearing. I have. The reverse dog claw 70b and the forward dog claw 70b are respectively provided on the left and right end surfaces of the shift sleeve 70.
a is formed.

Dog claws 67 for forward high speed and forward low speed
The axial distance between the a and 68a is secured to such an extent that the forward dog claw 70a of the sleeve 70 can be in a neutral state once.

A single shift fork 71 is fitted in the outer peripheral annular groove of the shift sleeve 70, and the shift fork 71 is fixed to the single shift rod 72, and the shift rod 72 is shifted to move in the left-right direction. It is supported by the machine case 11. The state of FIG. 5 shows a neutral state. When the shift sleeve 70 is moved leftward from the neutral state,
When the dog dog 70b for backward movement of the shift sleeve 70 meshes with the dog dog 69a of the gear 69 for reverse movement and moves rightward, the dog dog 70a for forward movement of the shift sleeve 70 firstly comes into contact with the dog nail of the gear 67 for forward high speed. The gear 67 is engaged with the dog claw 68a of the forward low-speed gear 68 through a neutral state. That is, by operating one shift fork 71, it is possible to switch to four speed stages of forward high speed, forward low speed, neutral and reverse.

At the right end of the shift rod 72, an upwardly projecting change pin 85 is provided. An inner change lever 86 is engaged with the change pin 85, and the inner change lever 86 is connected to a change lever shaft 87. It is connected to the outside change lever portion 35 through the above.

At the right end of the counter shaft 64, forward intermediate gears 73 and 74 that mesh with the forward high-speed and low-speed gears 67 and 68 are fixed, and at the left end, an intermediate output gear 75 is fixed.

A large-diameter first reverse gear 77 for engagement with the reverse gear 69 and a small-diameter second reverse gear 78 for engagement with the intermediate output gear 75 are fixed to the left end of the reverse idle shaft 65. Have been. The right half portion 65a of the reverse idle shaft 65 is formed to have a smaller diameter than the left half portion, and the outer peripheral surface of the small diameter right half portion 65a has the largest-diameter forward low-speed intermediate gear on the counter shaft 64. 74
Are as close as possible with a slight gap S2 therebetween. That is, the center distance between the counter shaft 64 and the reverse idle shaft 65 is configured to be as short as possible.

The intermediate output gear 75 meshes with an output gear 80 fixed to the left end of the output shaft 63, and the bevel gear 81 integrally formed on the right end of the output shaft 63
And is engaged with the bevel gear 82 fixed to the second gear.

[Vehicle speed sensor and forward / reverse determination sensor] A forward / backward determination sensor 111 is provided at the lower end of the transmission case 11.
And a vehicle speed sensor 110 are arranged separately on the left and right. The vehicle speed sensor 110 is fixed to a right end wall of the transmission case 11 and a bevel gear 82 fixed to the drive shaft 17.
Are arranged so as to face the outer peripheral surface from outside in the radial direction. The vehicle speed sensor 110 has a cable connection portion 1 facing backward.
10a is provided, and the electric wire cable 112 is detachably connected.

[0040]

[Operation] [Overall power transmission] In FIG.
Is transmitted to the front and rear propeller shafts 18 and 19 via a V-belt type continuously variable transmission 15, a gear type transmission 13, and a drive shaft 17, and the front and rear wheels 1, 2 via respective reduction gears. Is transmitted to

[Shift operation] The shift operation lever 3 shown in FIG.
By manually operating the lever 2, the outer change lever 35, the change lever shaft 87 and the inner change lever 86 in FIG. 5 are rotated via the connecting rod 33, whereby the shift rod is connected via the change lever pin 85. 72
Is moved in the direction of the rod axis O6 (left-right direction) to switch between forward low speed, forward high speed, neutral and reverse positions.

[Power transmission in the gear type transmission] When the gear position is the forward high speed position, that is, the shift sleeve 7 shown in FIG.
0 is moved to the right, and the dog dog pawl 70a for forward movement meshes with the dog pawl 67a of the gear 67 for high speed forward movement.
2 is transmitted from the forward high-speed gear 67 to the output shaft 63 via the forward high-speed intermediate gear 73, the counter shaft 64, the intermediate output gear 75, and the output gear 80.
Is rotated in the forward rotation direction, and the drive shaft 17 is rotated in the forward rotation direction via the bevel gears 81 and 82.

When the shift position is the forward low-speed position, that is, when the shift sleeve 70 is moved to the rightmost position and the forward dog pawl 70a and the dog pawl 68a of the forward low-speed gear 68 engage, the rotation of the input shaft 62 is stopped. The power is the forward low speed gear 6
8 to the output shaft 63 via the forward low-speed intermediate gear 74, the counter shaft 64, the intermediate output gear 75, and the output gear 80. The output shaft 63 is rotated in the forward rotation direction, and is transmitted through the bevel gears 81 and 82. To rotate the drive shaft 17 in the forward rotation direction.

When the gear position is the reverse position, that is, when the shift sleeve 70 is moved to the left, the reverse dog pawl 70b
When the dog claw 69a of the reverse gear 69 meshes with
The rotational force of the input shaft 62 is transmitted from the reverse gear 69 to the first reverse gear.
Idle gear 77, reverse idle shaft 65, second reverse
Idle gear 78, intermediate output gear 75, and output gear 80
, The output shaft 63 is rotated in the reverse rotation direction, and the drive shaft 17 is rotated through the bevel gears 81 and 82 in the reverse rotation direction. In the above-described reverse power transmission path, deceleration is performed between the reverse gear 69 and the first reverse idle gear 77, between the second reverse idle gear 78 and the intermediate output gear 75, and between the reverse gear 69 and the intermediate output gear 75. And the output gear 80, which is one more than in the case of the chain type. In addition, the diameters of the reverse first idle gear 77 and the reverse second idle gear 78 are made different. As a result, a large reduction ratio can be obtained without having an extremely large diameter reverse idle gear.

[0045]

[Other Embodiments] (1) The present invention can be applied to a gear type transmission of an engine of a type other than the V-type engine.

(2) It is also possible to make the length of the reverse idle shaft 65 in FIG.
In that case, the diameter of the forward low-speed intermediate gear 74 of the counter shaft 64 can be further increased.

[0047]

As described above, according to the invention described in the present application: (1) In a gear type transmission of an all-terrain vehicle, a reverse power transmission mechanism is also a gear type so that it can endure a large transmission torque. While maintaining the structure, the size of the transmission case in the transmission shaft center direction can be made smaller than that of the chain type. In particular, since the uneven terrain vehicle is of a riding type, if the size of the transmission case in the direction of the transmission shaft becomes compact, a large space for the rider's foot can be secured and the riding comfort is improved.

(2) A dog clutch which arranges a speed change input shaft and a speed change output shaft at an interval in the vertical direction, and switches between two forward speeds, neutral and reverse by moving a single shift sleeve on the speed change input shaft. By arranging the mechanism, a large space is provided for the intermediate shaft, and the counter shaft is arranged on the crankshaft side (front side) and the idle shaft is arranged on the rear side. The space in the crankcase (in the transmission case) between the shaft and the transmission input shaft can be efficiently used. The dimensions of the machine case in the direction perpendicular to the axis of the transmission shaft, particularly in the front-rear direction, can be compactly collected.

(3) A reverse idle shaft is provided together with the counter shaft as a shift intermediate shaft, and a reverse idle gear provided on the reverse idle shaft is a first reverse gear meshing with the reverse shift gear of the speed change input shaft. By providing the idle gear and the second reverse idle gear meshing with the intermediate output gear on the counter shaft, a reduction ratio can be obtained without using a large-diameter reverse reduction gear or a large-diameter chain wheel. This makes it possible to reduce the size of the transmission case in a direction perpendicular to the center axis of the transmission, for example, the size in the front-rear direction.

(4) If the two reverse idle gears on the reverse idle shaft are arranged close to one end in the direction of the axis of the transmission shaft, the two reverse idle gears are located near the support point of the bearing. Therefore, the influence of the shaft deflection is small, and the meshing accuracy of the reverse idle gear can be maintained. In addition, by assembling the two reverse idle gears to one side in the direction of the transmission axis, the ease of assembly of the reverse idle gear is also improved.

(5) The reverse idle shaft is supported at both end walls in the direction of the reverse idle shaft center of the transmission case, and a portion opposite to the side on which the first and second reverse idle gears are disposed is provided. When formed to have a small diameter, for example, by disposing the outer peripheral end of the intermediate gear for forward and low speed having the maximum outer diameter on the counter shaft close to the outer peripheral surface of the small diameter portion, the counter shaft and the reverse idle shaft Can be shortened, and the width of the transmission case in the front-rear direction and the like can be reduced.

[Brief description of the drawings]

FIG. 1 is a plan view of an all-terrain vehicle to which the present invention is applied.

FIG. 2 is a right side view of the off-road vehicle shown in FIG.

FIG. 3 is a left side view of the transmission case.

FIG. 4 is a longitudinal sectional view of a crankshaft portion of a crankcase.

FIG. 5 is a cross-sectional development view of the inside of the transmission case cut along a cut surface passing through each transmission shaft core.

FIG. 6 is a vertical left side view of a transmission case showing a transmission shaft arrangement.

FIG. 7 is an exploded cross-sectional view of a conventional example cut along a cutting plane passing through each transmission shaft core.

[Explanation of symbols]

 Reference Signs List 3 engine 10 crankcase 11 transmission case 13 gear type transmission 62 input shaft of gear type transmission 63 output shaft of gear type transmission 64 counter shaft 65 reverse idle shaft 67 forward high speed gear 68 forward low speed gear 69 reverse Gear 70 shift sleeve 71 shift arm 72 shift rod 73, 74 forward intermediate gear 75 intermediate output gear 77 reverse first idle gear 78 reverse second idle gear 80 output gear

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3J028 EA08 EA25 EB04 EB13 EB33 EB42 EB62 FB04 FC33 FC42 FC65 GA01 HA23

Claims (3)

[Claims] A transmission case integrally formed with a crankcase of an engine supports a transmission input shaft, a transmission output shaft, and a transmission intermediate shaft arranged in parallel with a crankshaft. In a gear-type transmission for an all-terrain vehicle, a dog clutch mechanism that switches between two forward speeds, neutral and reverse by moving a single shift sleeve is arranged on a speed change input shaft, and a speed change input shaft is used as a speed change intermediate shaft. A counter shaft having a forward intermediate gear meshing with each forward gear of the shaft; and a reverse idle shaft having a reverse idle gear meshing with the reverse gear of the speed change input shaft. The output shaft is vertically spaced within the transmission case, and a line connecting the transmission input shaft center and the transmission output shaft center between the transmission input shaft and the transmission output shaft. Close to the crankshaft A counter shaft disposed, terrain vehicle gear-type transmission, characterized in that is disposed a reverse idle shaft on the far side from the crankshaft. 2. The gear transmission according to claim 1, wherein the reverse idle gear includes a first reverse idle gear that meshes with the reverse gear of the speed change input shaft, and a counter idle shaft. A second reverse idle gear meshing with the intermediate output gear, wherein the first and second reverse idle gears are arranged closer to one end side in the axial direction of the reverse idle shaft. Gear transmission for all-terrain vehicles. 3. The gear transmission for an off-road vehicle according to claim 2, wherein the reverse idle shaft is supported at both end walls in the direction of the reverse idle shaft center of the transmission case, and the first idle shaft is provided with the first idle shaft. A gear-type transmission for an all-terrain vehicle, wherein a portion opposite to the side on which the second reverse idle gear is disposed has a small diameter.