JPH08320055A - Transmission of farm working machine - Google Patents

Abstract

PURPOSE: To miniaturize a transmission case by simply and compactly constitut ing a shifter mechanism. CONSTITUTION: When a shifter shaft C is axially moved by operating a shift lever, a power transmitting gear 15T is axially displaced by following it, a transmission path for power to be taken out to the output side is changed, and speed change can be performed. Since the power transmitting gear 15T is directly supported on the shifter shaft C, any shift fork is dispensed with, the shift fork needs not to be welded to the shaft, and only one shifter is required, and therefore, a shifter mechanism can be easily and compactly constituted, and miniaturization of a transmission case can be achieved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a speed change device for agricultural work machines adapted to perform tillage work and various management works.

[0002]

2. Description of the Related Art Conventionally, the transmission of this type of agricultural working machine has been
It is equipped with a shift lever that changes the vehicle speed and turns the tillage implement on and off.A shift fork that projects radially outward is connected to a shifter shaft that is displaced in the axial direction in conjunction with the operation of this lever. In addition, another shaft is arranged in parallel with the shifter shaft, the power transmission gear connected to the shift fork is splined to this shaft, and the shift fork connected to the shifter shaft is operated by operating the shift lever. The power transmission gear provided on the separate shaft is slid, and the power transmission path is changed according to the sliding position to change gears or the like.

[0003]

However, in the prior art, the shift fork is connected to the shifter shaft, and the assembly is complicated due to the need for welding or the like. In addition to the shifter shaft, the power transmission gear is also required. There is a problem that the cost increases and the size of the mission case increases because another shaft for supporting the shaft is required and there are two shafts. Further, there is a problem that a wear phenomenon or the like occurs in a portion where the shift fork and the gear are fitted together.

An object of the present invention is to provide a speed change device for an agricultural work machine in which a shifter mechanism can be configured simply and compactly and a mission case can be downsized.

[0005]

In order to achieve the above object, therefore, as shown in FIGS. 13 and 15, a shifter shaft C which is axially displaced in association with the operation of the shift lever 93 is provided. A power transmission gear 15T is provided, which follows the axial displacement of the shifter shaft C and is displaced in the axial direction, and changes the transmission route of the power taken out to the output side according to the displacement position.

[0006]

When the shift lever 93 is operated to move the shifter shaft C in the axial direction, the power transmission gear 15T follows the shifter shaft C.
Is displaced in the axial direction, the transmission path of the power taken out to the output side is changed, and gear shifting can be performed. Since the power transmission gear 15T is directly provided on the shifter shaft C, a shift fork is not necessary, and it is not necessary to weld this to the shaft, and since only one shaft is required, a shifter mechanism can be installed simply and compactly. Therefore, the mission case can be downsized. Furthermore, since there is no shift fork as in the conventional case, no wear or the like occurs and the durability is excellent.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The agricultural work machine shown in FIGS. 1 and 2 is a walking type management machine, and along the front-rear horizontal direction of the machine body 1, a tillage shaft 2 for driving a rotary tiller 20 from the front,
The engine 3, which is the drive source, and the axle 4, which drives the traveling wheel 40 including the pair of left and right wheels 41 and 42, are arranged in such a relationship that they appear in this order. A semi-loop-shaped handlebar 9 is extended rearward. The traveling wheel 40 is interposed between the operator who holds the handlebar 9 and the tiller 20,
Accidents such as accidental involvement of the operator in the tilling device 20 are prevented, and the safety of the operator can be ensured. The handlebar 9 may be extended rearward, or may be extended in the opposite direction as shown by an imaginary line.

The power of the engine 3 is transmitted to the input shaft E of the transmission case 5 via a pair of output / input pulleys 31 and 32 housed in the transmission case 30 and a belt 33 wound between them. Left and right wheels attached to 4
1, 42 are driven. Reference numeral 34 is a tension roller that constitutes a main clutch, and is a handlebar 9
The deadman clutch 91 that is supported by the clutch is used to engage and disengage. 35 is an engine cover, 36 is a muffler, 37
Is a fuel tank.

As shown in FIGS. 3 and 4, the fuel tank 37 has semicircular groove portions 37a and 37b on both left and right sides, and a concave groove portion 37c connecting the left and right sides on the lower surface. Then, from the loop portion 90 side of the handlebar 9 to the left and right parallel bar portions 9a and 9b, the semicircular groove portions 37a and 37b are formed.
7b is inserted, and a band 9c made of a steel strip or the like that is attached to the left and right parallel bar portions 9a and 9b with a screw 9d is fitted and locked in the groove 37c. Thus, while maintaining a compact and simple structure, the front and rear and left and right postures of the fuel tank 37 are well maintained, and
The support position of the fuel tank 37 with respect to the engine 3 is raised to eliminate the need for the fuel supply pump, and the distance from the engine 3 is increased to prevent the fuel from being carelessly applied to the muffler 36 and the like during refueling. ing.

Further, as shown in FIG. 1, there is provided a rotary case 6 for taking out power from the mission case 5 by branching the power to the tillage shaft 2.
A line segment L connecting the axle 4 and the tillage shaft 2 is included in the outer contour of the case, and is arranged substantially horizontally along the line segment L. The rotary case 6 and the mission case 5 are integrally formed by aluminum die casting.
More strictly speaking, as shown in FIGS. 5 and 6, two left and right divided cases 56a and 56b integrally provided with these two cases 5 and 6 are integrally formed by aluminum die casting. These divided cases 56a and 56b
Are butted against each other and connected by a large number of bolts 50.

The rotary tiller 20 driven by the tiller shaft 2 comprises a four-row tiller claw 21 which is composed of a ratchet claw.
And a substantially semi-cylindrical rotary cover 2 that covers the outer portion thereof
2, the rotary tiller 20 and the engine 3 are arranged in a relationship of overlapping each other in plan view as shown in FIG.

As shown in FIGS. 5 and 6, the rotary frame 11 for mounting the rotary cover 22 and the engine frame 12 for supporting the engine 3 are shared by the common frame 10 constituting the machine body 1. The rotary frame 11 includes left and right vertical plate members 11a and 11b that sandwich the rotary case 6 from the left and right,
Parts 50a, 50b, 50c, 50d of bolts 50 connecting the plate members 11a, 11b to the left and right split cases 56a, 56b forming the rotary case 6,
I try to tighten it together with 50e. Further, on the front part of each plate member 11a, 11b, left and right fixing pieces 11c, 1 for fixing the front part of the rotary cover 22 with bolts 11e.
1d is provided. The engine frame 12 includes plate members 11 a and 11 b that form the rotary frame 11.
A horizontal plate member 12a having a size corresponding to that of the engine base 38 is integrally fixed to the upper end of the rear portion, and four long holes 12 for mounting the engine 12 are formed in the plate member 12a.
b is provided. As shown in FIG. 5, the upper portion of the rotary cover 22 is fastened together with the engine 3 to the front two elongated holes 12b by bolts 12c. Thus
Generally, since the engine frame and the rotary frame are attached to the mission case respectively, it is necessary to fix the attachment portions extremely firmly. However, in this case, one plate 11 of each of the combined frames 10 is used.
Since a and 11b are connected to the rotary case 6, the rigidity can be sufficiently increased without fixing them extremely strongly.

Below the rotary tiller 20, as shown in FIG. 7, a V-shaped residual tiller 2 which plunges into the soil.
3a, an upward-opening U-shaped bracket 23c for fixing the same through a connecting rod 23b, and a horizontal stay 23d extending leftward and rightward at a rear portion of the residual tillage treatment device 23.
As shown in FIG. 5, the U-shaped bracket 23c is sandwiched below the rotary case 6, and the bolts 50c, 5 are inserted together with the plate members 11a, 11b.
The lower part of the rotary case 6 is prevented from being damaged by a stone bounce or the like. Further, the horizontal stay 23d and the rear portion of the rotary cover 22 are fixed by screws 23e to enhance the support rigidity of the rotary cover 22.

By the way, the rotary cover 22 has a semi-cylindrical portion 22a formed by blow molding with a synthetic resin material.
And the semi-circular plate portions 22b at both ends are integrally formed, and as shown in FIG.
In consideration of the protrusion of the fixed portion by 1e, 12c and the screw 23e, etc., the shape is formed along a smooth arc so that the flow of soil is improved as much as possible. That is, the degree of freedom in shape formation is increased by blow molding, and the inner surface 22c of the rotary cover 22 can be finished in a shape different from the outer surface. While considering the shape, its inner surface 22
c is finished in a smooth shape that can prevent soil adhesion,
It is designed so that the plowing work can be performed well.

At the foremost part of the machine body 1, FIG. 8, FIG. 9 and FIG.
As shown in Fig. 3, the support heights for the machine body 1 are three types of working heights, namely, a height 7a corresponding to deep tillage, a height 7b corresponding to standard tillage, and a height 7c corresponding to shallow tillage, and tillage is performed. Height 7 during non-working time when the machine 1 is moved in a place other than soil
Elevating wheels 7 that can be changed to d are provided. The lifting wheels 7 are a pair of left and right small wheels 7 connected by a connecting pipe 73.
In the inner part of the rotary cover 22, the rotary cover 22 is supported by the rotary arm 22 via the swing arm 70 so as to freely swing. Swing arm 70
Is the left and right plate members 11a, 11 that form the frame 10 with the base end side tubular portion 70a via the pivot pin 70b.
It is interposed between b, and the tip side cylinder portion 70c
A swivel shaft 74 extending upward from the connecting pipe 73 is inserted through the above, and this is locked by upper and lower locking bodies 75 and 76.
Reference numerals 77 and 78 are regulation bodies that regulate the left and right turning angles, and are integrally provided on the lower locking body 76.

The rocking pin 70 is attached to the swing arm 70.
An arm lock 710 having 00 is swingably supported via a pivot pin 70d, and this arm lock 710 is connected to an inner 921 of an operation wire 920 operated by an operation lever 92 supported on the handlebar 9, By swinging the arm lock 710 by an operation, both ends of the lock pin 700 are fixed to the inner surfaces of the plate members 11a and 11b on the lock plates 720 and 720, which correspond to the deep plowing groove 720a, the standard plowing groove 720b, and the shallow plowing. By engaging with either the corresponding groove 720c or the non-working corresponding groove 720d, the swing angle of the swing arm 70 is changed, and the support height of the lifting wheels 7 is changed.

Reference numeral 730 is a biasing member such as a spring that attaches the arm lock 710 to the lock plate 720 side, and is interposed in the pivot pin 70d. 740 is a support member that supports the outer 922 of the operation wire 920,
It is attached to the swing arm 10. By the way, the biasing body 73
0 is interposed in the part of the pivot pin 70d, and the support 74
It may be interposed between 0 and the tip of the inner 921 (imaginary line 730a). 750 and 760 are lock pins 7
Reference numeral 00 is a stopper that prevents the lock plate 720 from falling out of the arcuate movement range connecting the uppermost groove 720a and the lowermost groove 720d. Also, the lock plate 7
The inner surface 770 of 20 is formed by one arc centered at the position of the pivot pin 70b pivotally supporting the swing arm 70, and the disengagement direction 700a of the lock pin 700 with respect to each groove 720a. Lock plate 7 of lock pin 700
Coupled with the fact that the moving direction 700b with respect to 20 is made substantially orthogonal, unless the lever is operated,
The lock pin 700 is prevented from being inadvertently removed from each groove 720a .... Each groove 720a also has a pivot pin 70.
They are arranged in a constant arc shape centered on b.

In this way, by operating the operation lever 92, the supporting position of the lifting wheels 7 can be selected from three types corresponding to the plowing depth, and the rotary tilling device 20 sinks depending on the plowing depth. This makes it possible to properly prevent another attempt, and also receives the reaction force of the tilling claw 21 to generate a force for pressing the rear traveling wheel 40 against the ground, which makes dashing less likely to occur. . In addition, with a series of operations of the operation lever 92,
Since the working height can be changed to the moving height during non-working, the outer support 740 is attached to the swing arm 70, and the arm lock 710 is pivotally supported on the swing arm 70. Also, since the grooves 720a to 720d are arranged in an arc shape with the pivot pin 70b as the center,
When changing from any position to another position, the stroke of the operation wire 920 does not change, and the operation load can be substantially equalized. Further, the swing arm 70 is provided in a pair of the frame 10. Since it is arranged between the plate members 11a and 11b, it is possible to prevent the vertical movement of the lifting wheels 7 from being obstructed due to the adhesion of dirt, dirt clogging, etc. Further, when the lifting wheels 7 are supported, the rotary cover 22 is Since there are few members protruding to the outside, it is possible to reduce the adverse effects of soil adhesion as a whole. Moreover, in the working height of the lifting wheels 7, the distance between the grounding point of the lifting wheels 7 and the grounding point of the traveling wheels 40, that is, the front and rear wheel bases can be lengthened, so that stable work can be performed, and the height when not working is moved. Then, the wheel base can be shortened, and there is an advantage that it can be easily moved and swung.
Further, since the lift wheels 7 are arranged in front of the rotary tiller 20, the lift wheels 7 function as a bumper, so that the tiller 2 can be used when working in a house or the like.
It is also possible to prevent damage to the house etc. with 0.

In order to swingably support the lifting wheels 7, as shown in FIG. 11, the swinging arm 7 is formed on the upper portion of the rotary cover 22 so as to follow the outer shape of the cover 22.
0 is swingably supported via a pivot pin 70b, and a base end portion of the pin 70h is provided with an operation tool 70g provided at an end portion of an operation rod 70f having a screw 70e while allowing some play. And the operation rod 70f is moved forward and backward with respect to the fixed body 70j by the turning operation of the handle 70i.
The lifting wheels 7 may be adjusted up and down steplessly.

Mission case 5 constituting a power transmission unit
As shown in FIGS. 12 and 13, the rotary case 6 has a left and right output shafts A that constitute the axle 4, and a traveling side that is interlocked with the output shafts A through the sprockets 29T, 9TB and the chain C1 and has a gear 39T. Operation of the intermediate shaft B, the first shifter shaft C having an idle gear 15T that is displaced in the axial direction in association with the operation of the shift lever 93 and that is displaced in the axial direction following this axial displacement, and the operation of the shift lever 93. Second with a shift fork 12TF that is axially displaced in conjunction with
The input shaft E from the engine 3 that supports the shifter shaft D, the gear 12T that is axially displaced by the shift fork 12TF through the spline portion ES, the fixed gears 38TB and 9TA that transmit traveling power, and the rotary power. The intermediate shaft F having the idle gear 38TA for transmission, the rotary intermediate shaft G having the gear 24T, the sprocket 9TC,
It has an output shaft H which is a tilling shaft 2 which is interlocked via 14T and a chain C2.

As shown in FIG. 12, the shift lever 93 swings around a base shaft portion 93a and also rotates around an orthogonal shaft portion 93b orthogonal to the base shaft portion 93a. 93d, when the first shifter shaft C is in the neutral N position, the second shifter shaft D is rotated by the neutral N, the forward low speed F1 of rotary cutting without rotating the tiller shaft 2, and the tiller shaft 2. When the second shifter shaft D is in the position of neutral N while it is selectively moved to each position of the forward low speed F1on of the rotary entry, the first shifter shaft C does not rotate the neutral N and the tillage shaft 2 The rearward low speed R1 and the rearward low speed R1 on which the rotary shaft 2 is turned are turned on, and the forward high speed F2 when the rotary shaft is not turned and the rotary high speed F2 is selectively moved. .

As shown in FIG. 13, the shifter shafts C and D are provided with positioning grooves CM and DM corresponding to the respective shift stages, and as clearly shown in FIG.
Balls CB and DB attached by S and DS are engaged with each other. Moreover, between both shifter shafts C and D,
When the shifter shaft C or D on one side is moved by the two control balls B1 and B2, the control ball B2 or B1 facing the shifter shaft D or C on the non-moving side is moved to the groove DM or CM at the neutral N position. A restricting body BS for interposing the shifter shaft D or C on the side which is made to enter and is not moved at the neutral N position is interposed.

The idle gear 15T supported on the first shifter shaft C
Is a power transmission gear that is displaced in the axial direction following the axial displacement of the first shifter shaft C and changes the transmission route of the power taken out to the output side according to the displacement position. FIG.
As shown in FIG. 16, the washer W1 and the idling gear 15 which are engaged with the first shifter shaft C at the stepped portion of the first shifter shaft C are provided.
T, washer W2 and locking ring 1 interposed at the end
5TS, and the locking pin 15TP is inserted between the locking ring 15TS and the first shifter shaft C. As shown in FIGS. 14 and 15, the projecting portion of the locking pin 15TP has a pair of projections 5 projecting inward of the mission case 5.
1, 52 are provided so as to prevent the locking ring 15TS and thus the first shifter shaft C from rotating together with the rotation of the idle gear 15T.

Thus, when the forward speed is low F1, as shown in FIG. 13 or 17, the power from the input shaft E is 12T, 38TB, 9TA, 39T, 9TB, 2 when chased by a sign.
The power is transmitted in the order of 9T, and the output shaft A constituting the axle 4 is driven to rotate normally. At this time, as shown in FIG. 17, the idle gear 15T of the first shifter shaft C only idles, does not transmit power, and the idle gear 38TA that transmits rotary power transmits power. No, the tillage axis 2 does not rotate.

Further, at the time of the forward low speed F1on of the rotary input, as shown in FIG. 18, the power transmission path to the axle 4 side is the same, but the gear 12T and the idle gear 38T on the rotary side are the same.
It meshes with A, and in FIG. 13, 24T, 9TC, 1
The output shaft H, which is the tilling shaft 2, is rotated via 4T.

Further, at the time of low reverse speed R1, as shown in FIG. 19, the power of the gear 12T is once transmitted to the idle gear 15T and then to the fixed gear 38TB on the traveling side to idle the forward low speed F1. By interposing one gear 15T, the power for reverse rotation is transmitted to the axle 4 side.

Further, when the vehicle enters the rotary at a low reverse speed R1on, as shown in FIG. 20, the fixed gear 38TB on the traveling side and the idle gear 38 on the rotary side are passed through the idle gear 15T.
The reverse power is transmitted to the TA so that the tillage shaft 2 is also rotated in the reverse direction.

Further, at the forward high speed F2, as shown in FIG. 21, from the idle gear 15T to the gear 3 of the traveling side intermediate shaft B.
The power is directly transmitted to the 9T, and the high-speed forward rotation power is directly transmitted without the intermediate shaft F interposed.

The power transmission gear 15T supported on the first shifter shaft C is an idle gear, but as shown in FIG.
The receiving portion 93e of the shift lever 92 of the first shifter shaft C may be formed in an annular shape so that the first shifter shaft C rotates together with the gear 15T.

In the above, the left and right wheels 41, 42
23 and 2 in the middle of the power transmission path leading to
As shown in FIG. 4, between the left and right output shafts A constituting the axle 4 and the sprocket 29T, a cylindrical primary side transmission member 81 that integrates the sprocket 29T, and a disc-shaped primary side transmission surface facing the left and right end surfaces. A ball made of a steel ball that is movable to an engagement position (FIG. 23) that engages the secondary transmission member 82 with each other and a release position (release mechanism on the right side in FIG. 24) that releases this engagement. When the load acting on the secondary side transmission member 82 exceeds a predetermined value, the moving body 80
Is retracted from the engaged position to the disengaged position, and a pair of left and right connecting and disconnecting mechanisms 8 for interrupting power transmission are interposed.

More specifically, through holes 81a penetrating left and right are provided at several places, for example, three places in the circumferential direction of the cylindrical primary side transmission member 81, and inside each of these through holes 81a. , A pair of balls 80, 80 that are urged outward by the coil spring 80a to the left and right are provided, and the output shafts A constituting the axle 4 are provided in the left and right circular recesses 81b, 81b of the primary side transmission member 81. Disc-shaped secondary side transmission members 82, 82 for welding and fixing A are arranged respectively, and tears for receiving each ball 80 on the bottom surface of each secondary side transmission member 82 as shown in FIGS. 25 and 26. Shaped engagement groove 82a is provided.

By the way, in FIGS. 23 and 24, 8
Reference numeral 0b is a restriction pin that pushes and holds the ball 80 on the other side at the engaging position when the ball 80 on the left and right sides is in the release position, and 81c is an insertion hole that allows the output shaft A to slide.
2b is a washer for sliding the secondary transmission member 82, and 82c
Is a retaining ring. Instead of the coil spring 80a, a rubber body may be used, or the biasing force may be obtained by sealing the air in the through hole 81a. Further, instead of using the regulation pin 80b, the contact length of the coil spring 80a may be set so that the ball 80 on the other side is stretched to the engaging position when the ball 80 on one side is in the release position.

Thus, when the aircraft 1 travels straight ahead,
As shown in, the primary side transmission member 81 and the left and right secondary side transmission members 82 are engaged with each other, and the straightness thereof is maintained. on the other hand,
When the vehicle body 1 is turned, the wheels 4 on the side where the load is applied
Since a large load load for restraining the rotation acts on 1 or 42, a twist occurs between the secondary side transmission member 82 and the primary side transmission member 81 on the side where the large load acts, and FIG. As shown in FIG. 26, the ball 80 disengages from the engagement groove 82a, and finally, as shown in FIG. 24, the engagement between the primary side transmission member 81 and the secondary side transmission member 82 is released, Output shaft A on which the large load is applied
The power transmission to the machine is cut off, and a smooth turn can be made.
At the time of releasing the engagement, the engagement groove 82a has a teardrop shape, so that the ball 80 is smoothly released. Further, since the ball 80 transmits power until it is completely disengaged from the tear-shaped engagement groove 82a, the left and right wheels 41, 42 are not affected even if a slight uneven force is applied to the left and right wheels 41, 42. 42 turns at the same speed, and straightness is not impeded.

As shown in FIG. 26, the tear-shaped engaging groove 82a has a tapered surface for guiding the release of the ball only on one side in the circumferential direction. 26 may have a symmetrical groove shape, and both engaging grooves 82a may be provided with tapered surfaces as shown by an imaginary line in FIG. in this case,
In the teardrop shape, for example, the power is cut off smoothly only when the handlebar 9 is turned to the pushing side, while not only pushing out because both surfaces have tapered surfaces,
Pulling the handlebar 9 toward you also has the advantage that the power can be cut off smoothly.

[0035]

According to the invention described in claim 1, when the shift lever 93 is operated to move the shifter shaft C in the axial direction, the power transmission gear 15T is displaced in the axial direction following the shift, and the output is generated. Since the transmission path of the power taken out to the side is changed, gear shifting and the like can be performed, and the power transmission gear 15 is directly attached to the shifter shaft C.
Since T is provided, a shift fork is not required, and it is not necessary to weld this to a shaft, and since only one shaft is required, the shifter mechanism can be configured simply and compactly, and the shift case The size can be reduced, and since there is no shift fork, no wear phenomenon occurs and the durability is excellent.

[Brief description of drawings]

FIG. 1 is a side view of an agricultural work machine equipped with a transmission according to the present invention.

FIG. 2 is a plan view taken along line X and X of FIG.

FIG. 3 is a perspective view showing a procedure for attaching a fuel tank.

FIG. 4 is a perspective view showing a mounting state of a fuel tank.

FIG. 5 is a side view of a main part of the machine body.

FIG. 6 is a plan view of a main part of the machine body.

FIG. 7 is a perspective view of a residual tillage treatment device.

FIG. 8 is a side view of the lifting wheel portion.

FIG. 9 is a plan view of a lifting wheel portion.

FIG. 10 is a perspective view of a lifting wheel portion.

FIG. 11 is a side view showing a modified example of a support structure for lifting wheels.

FIG. 12 is an internal structural diagram of a power transmission unit in the transmission.

13 is a developed cross-sectional view taken along line Y, Y of FIG.

FIG. 14 is a sectional view of a detent portion on a shifter shaft.

FIG. 15 is a cross-sectional view of a power transmission gear portion of a shifter shaft.

FIG. 16 is an assembly view of a power transmission gear portion of the shifter shaft.

FIG. 17 is a gear state diagram when the rotary is turned off at a low forward speed.

FIG. 18 is a gear state diagram when the rotary is in a low forward speed.

FIG. 19 is a gear state diagram when the rotary is turned off and the vehicle is moving backward at a low speed.

FIG. 20 is a gear state diagram when the rotary is turned on and the vehicle is moving backward at a low speed.

FIG. 21 is a state diagram of gears when the rotary is turned off at a high forward speed.

FIG. 22 is a cross-sectional view of a modified example of the power transmission gear on the shifter shaft.

FIG. 23 is a cross-sectional view of the connecting / disconnecting mechanism that is interposed in the power transmission unit at the time of engagement.

FIG. 24 is a cross-sectional view at the time of releasing the relay mechanism that is interposed in the power transmission unit.

FIG. 25 is a bottom view of the secondary-side transmission member in the relay mechanism.

FIG. 26 is a cross-sectional view of a main part of a secondary side transmission member in the relay mechanism.

[Explanation of symbols]

93: shift lever, C: shifter shaft, 15T: power transmission gear

Claims (1)

[Claims] 1. A shifter shaft (C) which is axially displaced in association with an operation of a shift lever (93),
A transmission device for an agricultural work machine, which is provided with a power transmission gear (15T) that displaces in the axial direction following the axial displacement of the vehicle and changes the transmission path of the power taken out to the output side according to the displacement position. .