JP2009137327A - Working vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a working vehicle provided with PTO speed reduction mechanism capable of increasing a deceleration ratio and easily obtaining the number of revolution fitted to a working machine even when the number of revolution of an output shaft of an engine is high. <P>SOLUTION: In the cultivator 100, motive power of the output shaft 7a of the engine 7 is decelerated by the PTO speed reduction mechanism 26 and is transmitted to a cultivation device 2 through a PTO shaft 27. The PTO speed reduction mechanism 26 is provided with a speed reduction input shaft 35 arranged between the output shaft 7a and the PTO shaft 27; a belt type transmission mechanism 33 for transmitting the motive power of the output shaft 7a to the speed reduction input shaft 35; and a speed reduction gear case 34 internally installed with a speed reduction gear row 39 for decelerating the motive power of the speed reduction input shaft 35 and transmitting it to the PTO shaft 27. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a work vehicle technology in which power of an output shaft of an engine is decelerated by a PTO speed reduction mechanism and transmitted to a work machine via a PTO shaft, and more particularly to a technology of a PTO speed reduction mechanism.

2. Description of the Related Art Conventionally, in a work vehicle such as a riding field cultivator, the power of the output shaft of the engine is decelerated by a PTO reduction mechanism to obtain a rotational speed suitable for the work machine, and then transmitted to the PTO axis and a work machine such as a tillage device It is comprised so that it may drive (for example, refer to patent documents 1).
JP 2000-324904 A

  In the conventional work vehicle, the PTO speed reduction mechanism is constituted by a belt type using a pulley and a belt. In the case of the belt type, the reduction ratio can be increased by increasing the difference in pulley diameter by increasing the distance between the output shaft and the PTO shaft. There is a certain space limit. For this reason, even if it is possible to obtain a rotation speed suitable for the work implement in a range where the rotation speed of the output shaft of the engine is low, it is possible to obtain a rotation speed suitable for the work implement if the rotation speed is higher than a predetermined range. It was difficult.

  In view of the above situation, the present invention provides a work vehicle including a PTO reduction mechanism that can easily obtain a rotation speed suitable for a work machine even when the reduction ratio can be increased and the rotation speed of the output shaft of the engine is high. Objective.

  The problems to be solved by the present invention are as described above. Next, means for solving the problems will be described.

  That is, in claim 1, the working vehicle is configured such that the power of the output shaft of the engine is decelerated by the PTO deceleration mechanism and transmitted to the work machine via the PTO shaft, and the PTO deceleration mechanism includes the output shaft and the A deceleration input shaft disposed between the PTO shaft, a belt-type transmission mechanism that transmits the power of the output shaft to the deceleration input shaft, and the power of the deceleration input shaft is decelerated and transmitted to the PTO shaft. A speed reduction case having a speed reduction mechanism.

  According to a second aspect of the present invention, the speed reduction case is attached so as to be rotatable around the axis of the PTO shaft, and the output case and the speed reduction input shaft of the belt-type transmission mechanism are rotated by rotating the speed reduction case. The distance between the axes is changed.

  According to a third aspect of the present invention, the deceleration case is detachably attached to the PTO shaft.

  According to a fourth aspect of the present invention, the deceleration case is attached in a forward inclined posture around the PTO axis in a side view.

  As effects of the present invention, the following effects can be obtained.

  According to the first aspect of the present invention, the PTO speed reduction mechanism is composed of a belt type transmission mechanism and a speed reduction case, so that the speed reduction ratio can be increased as compared with the case where only the belt type transmission mechanism is decelerated, and the output shaft speed of the engine is high Even in this case, the number of rotations suitable for the work machine can be easily obtained.

  In claim 2, by rotating the speed reduction case and changing the distance between the output shaft and the speed reduction input shaft, the speed reduction ratio of the belt-type transmission mechanism can be changed and the rotation speed suitable for the work machine can be easily achieved. Is obtained.

  According to the third aspect, by replacing with a reduction case having a different reduction ratio, the number of rotations suitable for the work implement can be easily obtained, and maintenance is also easy.

  According to a fourth aspect of the present invention, the work case is prevented from hitting the speed reduction case when the work machine is lifted up by retracting the speed reduction input shaft side of the speed reduction case to the front of the machine body in the forward leaning posture. Therefore, it is possible to prevent the work implement from coming into contact with a bag or the like when the work vehicle turns.

Next, the best mode for carrying out the invention will be described.
1 is a side view showing a work vehicle, FIG. 2 is a side view showing a PTO reduction mechanism, FIG. 3 is a cross-sectional view showing an internal structure of the reduction case, and FIG. 4 is a side view showing a flange portion of a bearing pipe. FIG. 5 is a side view showing a state in which the distance between the output shaft and the deceleration input shaft of the belt-type transmission mechanism is changed, and FIG. 6 is a side view showing the positional relationship between the raised tiller and the deceleration case. FIG. 7 is a skeleton diagram showing the driving configuration of the crawler type traveling device and the tilling device, and FIG. 8A is a side view showing the stop arm in the clutch “ON” position. FIG. 7B is the stop arm in the clutch “OFF” position. FIG. 9 is a skeleton diagram showing the drive configuration of the deceleration case according to the first modification, and FIG. 10 is a skeleton diagram showing the drive configuration of the deceleration case according to the second modification.

First, the whole structure of the cultivator 100 which is a work vehicle is demonstrated using FIG.
As shown in FIG. 1, a cultivator 100 is a riding cultivator in which a cultivator 2 that is a work implement is attached to a rear portion of a traveling vehicle 1 via a work implement elevating device 3. In the following description, for the sake of convenience, the direction of the arrow A shown in FIG. In the present embodiment, a riding cultivator will be described as an example of a working vehicle. However, the working vehicle is not limited to a riding cultivator.

  In the traveling vehicle 1, a body frame 5 is disposed between the left and right of a pair of left and right crawler traveling devices 4. A driving unit 6 is disposed at the front of the fuselage frame 5, a transmission 8 is disposed at the rear of the fuselage frame 5, and on the rear side of the driving unit 6 (seat 24) above the transmission 8. An engine 7 that is a drive source of the tiller 100 is covered with a vehicle body cover 25 via a support device (such as a vibration isolator) (not shown). The traveling device of the traveling vehicle 1 is not limited to the crawler type but may be a tire type.

The crawler type traveling device 4 is configured such that the traveling vehicle 1 can travel by winding a crawler belt 15 around driving wheels 13, driven wheels 11, 12, and rolling wheels 14, 14, 14.
In the crawler type traveling device 4, a traveling frame 9 extends in the longitudinal direction of the machine body, and a driven wheel (front driven wheel) 11 is rotatably supported at an front end portion of the traveling frame 9 via an idler fork 10. A driven wheel (rear driven wheel) 12 is rotatably supported at the rear end of the traveling frame 9. Rolling wheels 14, 14, 14 are rotatably supported between the front driven wheel 11 and the rear driven wheel 12 of the traveling frame 9. A support frame 16 is erected on the rear portion of the traveling frame 9, and a drive shaft 8 a protruding from the transmission 8 to the left and right sides of the machine body is rotatably supported on the support frame 16. A drive wheel 13 is fixed to the end of the drive shaft 8a.

  The body frame 5 has a structure of the traveling vehicle 1 in which a guard frame 20 is installed on a frame (not shown) formed in a substantially rectangular frame shape in plan view. The guard frame 20 is formed such that a round pipe is bent and inclined in a substantially U-shape at the rear opening in a plan view and to a front low rear height in a side view.

  In the operation unit 6, a step 21 is formed at the front end of the guard frame 20, and a handle column 22 is erected on the step 21. A steering handle 23 is attached to the handle column 22 via a support shaft (not shown). A seat 24 is disposed behind the steering handle 23. On the side of the seat 24, levers such as a main / sub transmission lever (not shown) and a PTO clutch lever 45 (see FIG. 2) are arranged.

  The engine 7 has an output shaft 7a (a cam shaft or a crankshaft) that projects to the side of the machine body (to the left in this embodiment) and outputs power. The power of the output shaft 7a of the engine 7 is transmitted to the transmission shaft 8b of the transmission 8 via the transmission mechanism 31, and to the PTO shaft 27 via the PTO reduction mechanism 26 (belt type transmission mechanism 33, reduction gear case 34). It is configured to be transmitted.

  The transmission mechanism 31 includes an output pulley 28 fixed on the output shaft 7a, an input pulley 30 fixed on the transmission shaft 8b, and a belt 32 wound around the output pulley 28 and the input pulley 30. And is configured to be capable of transmitting power.

  The PTO shaft 27 is a shaft for taking out the power of the engine 7 for driving the tilling device 2. The PTO shaft 27 is rotatably provided in a bearing pipe 56 (see FIG. 3) disposed in the rear portion of the body frame 5 with the body left-right direction as an axial direction.

  The transmission 8 has a transmission shaft 8b that protrudes to the side of the machine body (leftward in this embodiment) and transmits the power of the engine 7, and is configured to transmit the power of the transmission shaft 8b to the drive shaft 8a. Has been.

The work machine lifting / lowering device 3 includes a lifting / lowering arm 57 rotatably supported by the bearing pipe 56 (see FIG. 3), and a hydraulic pressure interposed between the lifting / lowering arm 57 and the rear portion of the guard frame 20. And a cylinder 58. A hitch 60 to which the tilling device 2 is attached is provided at the rear of the lifting arm 57.
In the work machine lifting / lowering device 3, the lifting / lowering valve (not shown) is switched by the operation of a position lever (not shown) disposed in the vicinity of the seat 24, and the hydraulic oil from the hydraulic pump 59 (see FIG. 7) is supplied to the hydraulic cylinder. When oil is fed to 58, the hydraulic cylinder 58 is expanded and contracted, and the lifting arm 57 is rotated about the axis of the PTO shaft 27 to move up and down.

The tilling device 2 includes a tilling shaft 61 whose axial direction is the left-right direction of the machine body, a plurality of tilling claws 62, 62,... Planted at predetermined intervals in the axial direction of the tilling shaft 61. And a cover 76 covering 62.
In the tillage device 2, an input shaft 63 having an axial direction in the horizontal direction of the machine body is disposed between the tillage shaft 61 and the PTO shaft 27, and the power of the PTO shaft 27 is the first chain case 64 (see FIG. 7). The plurality of tilling claws 62, 62,... Are driven by being transmitted to the tilling shaft 61 through the input shaft 63 and the second chain case 68.

Next, the PTO deceleration mechanism 26 will be described with reference to FIGS.
As shown in FIG. 2, the PTO deceleration mechanism 26 decelerates and transmits the deceleration input shaft 35 disposed between the output shaft 7 a and the PTO shaft 27 and the power of the output shaft 7 a to the deceleration input shaft 35. A belt-type transmission mechanism 33 and a reduction gear case 34 that is a reduction case in which a reduction gear train 39 that is a reduction mechanism for further reducing the power of the reduction input shaft 35 and transmitting it to the PTO shaft 27 is provided.

The belt-type transmission mechanism 33 is wound around an output pulley 36 fixed on the output shaft 7 a, an input pulley 37 fixed on the right end portion on the deceleration input shaft 35, and the output pulley 36 and the input pulley 37. And a belt 38 that is configured to decelerate the power of the output shaft 7a and transmit it to the deceleration input shaft 35. The belt-type transmission mechanism 33 includes a clutch mechanism 42, and is configured to transmit or block the power of the output shaft 7a to the deceleration input shaft 35.
The belt-type transmission mechanism 33 according to this embodiment is configured to decelerate the power of the output shaft 7a and transmit it to the deceleration input shaft 35. However, the power of the output shaft 7a is transmitted to the deceleration input shaft 35 at a constant speed. The structure to do may be sufficient.

  The reduction gear case 34 includes a reduction gear train 39 interposed between the reduction input shaft 35 and the PTO shaft 27, and a case 40 that houses the reduction gear train 39. The speed is further reduced by the reduction gear train 39 and then transmitted to the PTO shaft 27.

As shown in FIG. 3, the case 40 is configured by joining left and right half cases 40L and 40R with bolts (not shown).
On one side in the longitudinal direction of the reduction gear case 34 (upper side in FIG. 3), the left end portion of the reduction input shaft 35 is rotatably supported by the case 40 via bearings 35a and 35a. A spline portion is formed at the right end portion of the deceleration input shaft 35, and an input pulley 37 is fitted to the spline portion so as not to be relatively rotatable, and is fixed by a bolt 37a or the like. Here, the reduction input shaft 35 to which the input pulley 37 is fixed and the reduction gear case 34 constitute an integral unit.
The left end portion of the PTO shaft 27 is rotatably supported by the case 40 via bearings 27a and 27a on the other side in the longitudinal direction of the reduction gear case 34 (lower side in FIG. 3).

  The reduction gear train 39 includes a drive gear 39a fixed to the left end portion on the reduction input shaft 35, a driven gear 39b fixed to the left end portion on the PTO shaft 27, a drive gear 39a, and a driven gear 39b. An idle gear 39c that meshes. The driven gear 39b is fitted to a spline portion formed at the left end portion on the PTO shaft 27 protruding from the left side portion of the bearing pipe 56 so as not to be relatively rotatable. The idle gear 39c is fitted to a spline portion formed on the idle shaft 41 so as not to be relatively rotatable. The idle shaft 41 is rotatably supported by the case 40 via bearings 41a and 41a.

Next, a configuration for attaching the reduction gear case 34 to the bearing pipe 56 will be described with reference to FIGS.
As shown in FIG. 4, the bearing pipe 56 is a pipe member having a circular shape in a side view in which the PTO shaft 27 is rotatably provided. A flange portion 56 a to which the case 40 of the reduction gear case 34 is attached is fixed to the left end portion on the bearing pipe 56.
The flange part 56a is a collar part having a circular shape in a side view. In the flange portion 56a, a plurality of (four in this embodiment) long holes 56b, 56b,... Having a predetermined circumferential length are formed at equal intervals on the same circumference (radius) in side view. .

On the other hand, returning to FIG. 3, on the reduction gear case 34 side, an attachment portion 40b attached to the bearing pipe 56 is formed on the right side surface of the case 40R facing the flange portion 56a.
The mounting part 40b has a convex part in a side view circular shape that fits on the inner periphery of the bearing pipe 56, and a mounting surface in a donut shape in a side view that faces the flange part 56a around the convex part. . On the mounting surface of the mounting portion 40b, the same number as the long holes 56b, 56b,... On the same circumference (radius) in side view according to the position of the long holes 56b, 56b,. Four bolts 72, 72... Are embedded and fixed and protrude rightward.

With such a configuration, the reduction gear case 34 (the unit including the reduction input shaft 35 and the input pulley 37) is attached to the bearing pipe 56 and the PTO shaft 27 as follows.
In the reduction gear case 34, the left end portion (spline portion) of the PTO shaft 27 is fitted into the driven gear 39b, whereby the driven gear 39b is fitted into the PTO shaft 27 so as not to be relatively rotatable. The reduction gear case 34 is supported by the PTO shaft 27 and the bearing pipe 56 so as to be rotatable about the axis of the PTO shaft 27 by fitting the convex portion of the mounting portion 40 b to the inner periphery of the bearing pipe 56.
The bolts 72, 72,... Are inserted into the long holes 56b, 56b,... Of the flange portion 56a, and are fastened and fixed with nuts 78, 78, so that the reduction gear case 34 is fixed to the bearing pipe 56. The At this time, when the nuts 78, 78... Are loosened, the reduction gear case 34 is rotated around the axis of the PTO shaft 27 within the peripheral length of the long holes 56b, 56b. Can be made. Thus, by changing the inter-axis distance L between the output shaft 7a and the deceleration input shaft 35 in the belt-type transmission mechanism 33, the effective diameters of the output pulley 36 and the input pulley 37 are changed, and the belt-type transmission mechanism 33 is decelerated. The ratio is changed.

Here, when the input pulley 37 on the deceleration input shaft 35 is replaced to change the reduction ratio, the belt 38 needs to be replaced due to the change of the belt length accompanying the replacement of the input pulley 37, resulting in an increase in cost. In addition, when the reduction range is changed by changing the rotation range of the tension arm 44, the link length to be described later is changed, so that the cost is similarly increased.
On the other hand, when changing the reduction ratio by changing the inter-axis distance L as in the present invention, there is no need to replace the belt 38 or change the link length, so that the cost is not increased. Further, the reduction gear case 34 can be easily detached from the bearing pipe 56 by removing the nuts 78. That is, the reduction gear case 34 can be easily attached to and detached from the bearing pipe 56 (PTO shaft 27).

The reduction gear case 34 is attached in a forward inclined posture around the axis of the PTO shaft 27 in a side view.
As shown in FIG. 6, the speed reduction gear case 34 has a center line X (a line connecting the speed reduction input shaft 35 and the PTO shaft 27) inclined at an angle θ from the vertical line to the front of the body around the axis of the PTO shaft 27 in the side view. Attached. In the reduction gear case 34, the reduction input shaft 35 is located in front of the rear surface 77 of the traveling vehicle 1.
With such a configuration, the reduction gear case 34 is tilted forward, and the upper part (the reduction input shaft 35 side) of the reduction gear case 34 is retracted forward of the body. Thereby, when the tillage device 2 is raised, the front portion of the tillage device 2 (such as the cover 76) can be prevented from hitting the reduction gear case 34 and the tillage device 2 can be lifted high. It is possible to prevent the device 2 from coming into contact with a bag or the like.

Next, drive configurations of the crawler type traveling devices 4 and 4 and the tilling device 2 will be described with reference to FIG.
As shown in FIG. 7, the power of the engine 7 is transmitted to the crawler type traveling devices 4 and 4 via the output shaft 7a, the transmission mechanism 31 (the output pulley 28, the belt 32, the input pulley 30), and the transmission shaft 8b. 8 is transmitted. In the transmission 8, the power of the transmission shaft 8 b is shifted and transmitted to the drive shafts 8 a and 8 a by a main transmission and a sub transmission (not shown) provided inside, and the rotation direction of the drive shafts 8 a and 8 a is switched by a forward / reverse clutch. It is like that. A pump shaft 59a of a hydraulic pump 59 for extending and contracting the hydraulic cylinder 58 is connected to the right end portion of the transmission shaft 8b so that power can be transmitted.
Then, the power of the drive shafts 8a and 8a is transmitted to the drive wheels 13 and 13, the crawler belt 15 and the like, and the crawler type traveling devices 4 and 4 are driven.

Next, the power of the engine 7 is output to the tilling device 2 side by the output shaft 7a, the belt type transmission mechanism 33 (output pulley 36, belt 38, input pulley 37), the reduction input shaft 35, and the reduction gear train 39 of the reduction gear case 34 ( It is transmitted to the PTO shaft 27 via a drive gear 39a, an idle gear 39c and a driven gear 39b).
The power of the PTO shaft 27 is transmitted from the drive sprocket 65, the chain 67, and the driven sprocket 66 in the first chain case 64 to the input shaft 63, and the power of the input shaft 63 is transmitted to the drive sprocket 69 in the second chain case 68. The chain 71 and the driven sprocket 70 are transmitted to the tilling shaft 61, and the power of the tilling shaft 61 is transmitted to the tilling claws 62, 62... To drive the tilling device 2.

  The first chain case 64 includes a drive sprocket 65 fixed to the right end portion on the PTO shaft 27, a driven sprocket 66 fixed to the right end portion on the input shaft 63, and the drive sprocket 65 and the driven sprocket 66. A power transmission means including a wound chain 67 is provided so that the power can be transmitted.

  The second chain case 68 includes a drive sprocket 69 fixed to the left end portion on the input shaft 63, a driven sprocket 70 fixed to the center portion on the tilling shaft 61, and the drive sprocket 69 and the driven sprocket 70. A power transmission means provided with a wound chain 71 is provided so as to be able to transmit power.

Next, the clutch mechanism 42 of the belt-type transmission mechanism 33 will be described with reference to FIG.
Here, referring back to FIG. 2, the clutch mechanism 42 includes a tension arm 44 having a tension roller 43 and a link mechanism 46 that swings the tension arm 44 by operating the PTO clutch lever 45.

  One end of the tension arm 44 is rotatably supported by an arm shaft 44a having an axial direction in the horizontal direction of the machine body below the belt 38. A tension roller 43 that applies tension to the belt 38 is rotatably supported at the other end of the tension arm 44, and the tension roller 43 is configured to contact the lower surface of the belt 38.

  The link mechanism 46 is interposed between the PTO clutch lever 45 and the tension arm 44. The link mechanism 46 is configured to swing the tension arm 44 when the PTO clutch lever 45 is operated. The base portion of the PTO clutch lever 45 is rotatably supported by a lever shaft 45a whose axial direction is the left-right direction of the machine body.

In the link mechanism 46, one end portion of the link arm 48 is fixed to the end portion of the tension arm 44 and is rotatably supported on the arm shaft 44a. Between the arm shaft 44a and the lever shaft 45a, a link shaft 49 having an axial direction in the lateral direction of the machine body is disposed.
One end of the link arm 50 and the link arm 51 is rotatably supported on the link shaft 49, and a tension spring 47 is provided between the other end of the link arm 50 and the other end of the link arm 48. The end of each is locked.

  Further, as shown in FIG. 8A, one end of the stay 54 is rotatably supported on the lever shaft 45 a, and one end of the link arm 53 is connected to the base of the PTO clutch lever 45. It is fixed and supported rotatably on the lever shaft 45a. Side ends of a boomerang-like tension lever 52 are rotatably attached to the other end of the link arm 53 and the other end of the link arm 51, respectively.

  One end of a hook 55 is rotatably attached to the link arm 53. The hook 55 is biased counterclockwise as viewed from the side by a torsion spring (not shown). A locking groove 55 a that can be locked to a locking pin 54 a that protrudes at the tip of the stay 54 is formed at the other end of the hook 55. Then, the link arm 53 and the stay 54 are urged so as to approach each other by a torsion spring (not shown) so that the hook 55 (locking groove 55a) is locked to the stay 54 (locking pin 54a). It has become.

With this configuration, when the PTO clutch lever 45 is rotated from the clutch “disengaged” position shown in FIG. 2 to the clutch “on” position, the link arm 53 is rotated counterclockwise as viewed from the side, and the tension lever 52 and the tension spring 47 are pulled forward. The PTO clutch lever 45 (stay 54) exceeds the fulcrum and is held at the clutch “ON” position.
When the tension spring 47 is pulled forward, the link arm 48 and the tension arm 44 are rotated clockwise in a side view, the tension roller 43 applies tension to the belt 38, and the belt transmission mechanism 33 transmits power. Then, the power of the output shaft 7a is transmitted to the PTO shaft 27.

  Next, when the PTO clutch lever 45 is rotated from the clutch “on” position to the clutch “disengaged” position, the tension arm 44 is rotated counterclockwise as viewed from the side by the reverse operation to the tension roller 43. The tension applied to the belt 38 to be applied is eliminated, the belt type transmission mechanism 33 enters a power cut-off state, and the power from the output shaft 7a to the PTO shaft 27 is cut off.

Here, as shown in FIG. 8 (a), a stop pin 55 b protrudes to the left at the tip of the hook 55, and the stop near the base of the PTO clutch lever 45 is on the stop side. A stop arm 73 that is in contact with the lower side of the pin 55b is rotatably provided. A clutch pedal 75 disposed on the step 21 of the operating unit 6 is linked to the stop arm 73 via a stop wire 74.
The stop arm 73 is a plate-like member formed in a substantially L shape in a side view, and one end thereof is rotatably supported by an arm shaft 73a whose axial direction is the left-right direction of the body. One end of a stop wire 74 is attached to the bent portion of the stop arm 73.
The clutch pedal 75 is rotatably supported by a pedal shaft 75a whose base is the left-right direction of the body. One end of a pedal arm 75b is fixed to the pedal shaft 75a, and the other end of the stop wire 74 is attached to the other end of the pedal arm 75b. The clutch pedal 75 is also linked to a clutch of a travel unit (not shown).

Then, in a state where power is transmitted from the output shaft 7a to the PTO shaft 27, the power can be urgently interrupted by depressing the clutch pedal 75.
Specifically, when the clutch pedal 75 is depressed, the stop wire 74 is pulled forward via the pedal shaft 75a and the pedal arm 75b.
Then, when the stop wire 74 is pulled forward, the stop arm 73 is rotated clockwise as viewed from the side (as viewed from FIG. 8A) with the arm shaft 73a as an axis in a state where the tip portion is in contact with the stop pin 55b of the hook 55. 8 (b)), whereby the hook 55 is detached from the locking pin 54a.
At this time, since the tension lever 52 does not exceed the fulcrum, the link arm 53 and the PTO clutch lever 45 are rotated about the lever shaft 45a by the urging force of the tension spring 47, and the clutch is moved from the clutch “on” position. It is turned to the “OFF” position. The hook 55 released from the locking pin 54a is again locked to the locking pin 54a by the biasing force of the torsion spring (not shown).
Thus, as described above, the belt-type transmission mechanism 33 enters the power cut-off state, and the power is cut off from the output shaft 7a to the PTO shaft 27. When the link arm 53 is rotated, the stay 54 is rotated to the clutch “disengaged” position by the urging force of the torsion spring interposed between the link arm 53 and the stay 54. Yes.

As described above, the tiller 100 is a work vehicle in which the power of the output shaft 7a of the engine 7 is decelerated by the PTO reduction mechanism 26 and transmitted to the tilling device 2 via the PTO shaft 27. Includes a deceleration input shaft 35 disposed between the output shaft 7a and the PTO shaft 27, a belt-type transmission mechanism 33 that transmits the power of the output shaft 7a to the deceleration input shaft 35, and the power of the deceleration input shaft 35. A reduction gear case 34 having a reduction gear train 39 that decelerates and transmits it to the PTO shaft 27.
With such a configuration, the speed reduction ratio can be made larger than when the PTO speed reduction mechanism 26 is decelerated only by the belt-type transmission mechanism 33, and the rotation speed suitable for the tillage device 2 even when the output shaft 7a of the engine 7 is high. Is easily obtained.

The reduction gear case 34 is attached so as to be rotatable about the axis of the PTO shaft 27. When the reduction gear case 34 rotates, the distance between the output shaft 7a and the reduction input shaft 35 in the belt-type transmission mechanism 33 is reduced. L is to be changed.
With such a configuration, the effective diameter of the output pulley 36 and the input pulley 37 can be changed by rotating the reduction gear case 34 to change the inter-axis distance L between the output shaft 7a and the reduction input shaft 35. By changing the speed reduction ratio of the mechanism 33, a rotational speed suitable for the tilling device 2 can be easily obtained.

The reduction gear case 34 is detachably attached to the PTO shaft 27.
With such a configuration, by replacing the reduction gear case 34 with a reduction gear case having a different reduction ratio, the number of rotations suitable for the tilling device 2 can be easily obtained, and maintenance is also easy.

The reduction gear case 34 is attached in a forward inclined posture around the axis of the PTO shaft 27 in a side view.
With such a configuration, when the speed reduction gear case 34 is tilted forward and the speed reduction input shaft 35 side of the speed reduction gear case 34 is retracted forward of the fuselage, the power tiller 2 hits the speed reduction gear case 34 when the power tiller 2 is raised. Therefore, it is possible to prevent the tilling device 2 from coming into contact with the straw or the like when the tiller 100 is turned.

In addition, embodiment is not limited above, For example, you may change as follows.
For example, like the reduction gear case 134 according to the first modification shown in FIG. 9, depending on the rotational direction of the output shaft 7a of the engine 7, the reduction mechanism can be configured by a reduction gear train 139 that does not use an idle gear. . The reduction gear train 139 includes a drive gear 139a and a driven gear 39b that meshes with the drive gear 139a.

  Further, the speed reduction mechanism can be configured by a chain type speed reduction mechanism 239 as in the speed reduction chain case 234 according to the second modification shown in FIG. The chain type speed reduction mechanism 239 includes a drive sprocket 239a, a driven sprocket 239b, and a chain 239c wound around the drive sprocket 239a and the driven sprocket 239b, and is configured to transmit power.

  Further, the circumferential length and the number of the long holes 56b, 56b,... Formed in the flange portion 56a of the bearing pipe 56 shown in FIG. 4 are not limited to the present embodiment. For example, by increasing the peripheral length of the long holes 56b, 56b,..., The rotation angle of the reduction gear case 34 can be increased and the adjustment range of the reduction ratio can be increased, and the long holes 56b, 56b,. By increasing the number of bolts 72, 72..., The reduction gear case 34 and the bearing pipe 56 can be more reliably attached.

The side view which showed the work vehicle. The side view which showed the PTO deceleration mechanism. Sectional drawing which showed the internal structure of the deceleration case. The side view which showed the flange part of the bearing pipe. The side view which showed the state from which the center distance of the output shaft of a belt-type transmission mechanism and a deceleration input shaft changes. The side view which showed the positional relationship of the raised tiller and the deceleration case. The skeleton figure which showed the drive structure of the crawler type traveling device and the tillage device. (A) Side view showing stop arm in clutch “on” position (b) Side view showing stop arm in clutch “off” position. The skeleton figure which showed the drive structure of the deceleration case which concerns on a 1st modification. The skeleton figure which showed the drive structure of the deceleration case which concerns on a 2nd modification.

Explanation of symbols

2 Tillage device (work machine)
7 Engine 7a Output shaft 26 PTO reduction mechanism 27 PTO shaft 33 Belt transmission mechanism 34 Reduction gear case (deceleration case)
35 Reduction input shaft 39 Reduction gear train (reduction mechanism)
100 cultivator (work vehicle)
134 Reduction gear case (deceleration case)
139 Reduction gear train (reduction mechanism)
234 Deceleration chain case (deceleration case)
239 Chain type deceleration mechanism (deceleration mechanism)

Claims (4)

A work vehicle in which the power of the output shaft of the engine is decelerated by the PTO reduction mechanism and transmitted to the work implement via the PTO shaft;
The PTO deceleration mechanism is
A deceleration input shaft disposed between the output shaft and the PTO shaft;
A belt-type transmission mechanism that transmits power of the output shaft to the deceleration input shaft;
A deceleration case that includes a deceleration mechanism that decelerates the power of the deceleration input shaft and transmits it to the PTO shaft,
A working vehicle characterized by that. The deceleration case is attached so as to be rotatable about the PTO axis.
By rotating the deceleration case, the distance between the output shaft and the deceleration input shaft in the belt-type transmission mechanism is changed.
The work vehicle according to claim 1. The deceleration case is detachably attached to the PTO shaft.
The work vehicle according to claim 1, wherein the work vehicle is a vehicle. The deceleration case is attached in a forward inclined posture around the PTO axis in a side view.
The work vehicle according to any one of claims 1 to 3, wherein the work vehicle is a vehicle.

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