JP2018000090A - Transmission of working machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To miniaturize a work case unit by devising a drive side rotary member, a driven side rotary member, a clutch operation member and an arrangement structure of a pushing spring.SOLUTION: A work clutch 8 in a work case unit 4 includes a drive side rotary member 80, a driven side rotary member 81 and a pushing spring 82. A clutch operation member 83 is included which is engaged with an engagement part 81c in an outer circumferential side of the driven side rotary member 81, and can operate the driven side rotary member 81 to the side separated from the drive side rotary member 80 against the pushing spring 82. The pushing spring 82 is equipped in the inside in the radial direction rather than an engagement place between the clutch operation member 83 and the engagement part 81c.SELECTED DRAWING: Figure 4

Description

  The present invention is provided with a main body part that outputs shifting power to a traveling drive system and a work case part that outputs shifting power to a work device, on a traveling machine body that can move and move in a field. The present invention relates to a transmission device for a work machine in which a work clutch capable of intermittently transmitting power from a system transmission mechanism to a work drive shaft is incorporated.

  In providing the work clutch, in the conventional structure, the engagement portion between the drive side rotation member and the driven side rotation member, the engagement portion of the clutch operation member with respect to the driven side rotation member, and the pressing spring are provided in the work case portion. In the axial direction of the output shaft (see Patent Document 1).

JP 2008-173087 A (see paragraph numbers “0038” and “0039”, FIG. 5 and FIG. 7)

  In the transmission device of the working machine described in Patent Document 1 described above, there is a space corresponding to the sum of the axial length of the driving-side rotating member, the axial length of the driven-side rotating member, and the axial length of the pressing spring. Necessary on the output shaft in the work case section, there is room for improvement in that it is difficult to miniaturize the transmission.

  The present invention intends to further reduce the size of the work case portion by devising the arrangement structure of the driving side rotation member, the driven side rotation member, the clutch operation member, and the pressing spring in the work case portion.

The power transmission device for a working machine according to the present invention is characterized in that a main case portion that includes a speed change mechanism that changes the input engine power and outputs the speed change power to the traveling drive system, and the engine power input via the main case portion. And a work case portion that outputs gear shift power to the work device, and the work case portion transmits gear shift power from the work gear shift mechanism to the work device. And a work clutch capable of intermittently transmitting power from the work system transmission mechanism to the work drive shaft, and the work clutch is located on the upper side in the power transmission direction. A drive-side rotating member to which the power from the drive side is transmitted, and the work-side drive shaft is externally fitted to the work drive shaft on the lower side in the power transmission direction than the drive-side rotary member, and is supported on the work drive shaft so as to be integrally rotatable. A driven side rotational member provided with a,
The driving-side rotating member and the driven-side rotating member are formed with meshing portions capable of transmitting power in a meshed state on the respective opposing surfaces, and the driven-side rotating member with respect to the driving-side rotating member The rotating member is configured to be movable in the near-and-far direction along the axial direction of the work drive shaft, and a pressing spring that presses and biases the driven side rotating member toward the drive side rotating member is fitted on the work drive shaft. A clutch operating member that is operable to move the driven-side rotating member away from the driving-side rotating member against the urging force of the pressing spring, and the clutch operating member rotates the driven-side rotation It is configured to engage with an engaging portion formed on the outer peripheral side of the member so that the driven side rotating member can be operated away from the driving side rotating member, and the pressing spring is connected to the clutch operating member and the engaging member. Is that is equipped inward in the radial direction of the driven side rotational member than the engaging portion between the parts.

  According to the present invention, the abutting position of the pressing spring with respect to the driven-side rotating member is set in the radial direction from the engaging position without being restricted by the position where the engaging position between the clutch operating member and the engaging portion exists. Therefore, there is an advantage that the internal space of the work case portion in the moving direction of the driven side rotation member can be easily shortened while using a pressing spring having a required length.

  In the present invention, a spring receiving portion is formed on a surface opposite to the side on which the meshing portion of the driven side rotating member is formed, and the spring receiving portion is operated in the axial direction of the work drive shaft in the clutch operation. It is preferable that it is provided at a location closer to the facing surface where the meshing portion is formed than an engagement location between the member and the engagement portion.

  According to the present invention, the spring receiving portion is provided in a position closer to the facing surface side where the meshing portion is formed than the engagement portion between the clutch operating member and the engagement portion in the axial direction of the work drive shaft. Thus, the driven-side rotating member and the pressing spring can be overlapped in the moving direction of the driven-side rotating member, so that the internal space of the work case portion can be shortened reliably.

  In the present invention, the pressing spring is mounted between the spring receiving portion and the fixed portion on the inner surface side of the work case portion, and is closer to the other end side than the one end side in the axial direction of the work drive shaft. It is suitable if it is formed in a truncated cone shape with a large winding diameter.

  By providing this configuration, it becomes difficult for the pressing spring to be deformed such as bending in a direction intersecting the expansion and contraction direction, and the spring force can be easily exerted accurately.

  In the present invention, the pressing spring is formed such that a winding diameter on the side supported by the spring receiving portion of the driven side rotation member is larger than a winding diameter on the opposite side, and the winding diameter on the opposite side. Is preferably set to such an extent that the inner peripheral surface of the pressing spring contacts the outer peripheral surface of the work drive shaft.

  By providing this configuration, the winding diameter on the side supported by the spring receiving portion is increased, the winding diameter on the opposite side is decreased, and the pressing spring is set so as to contact the outer peripheral surface of the work drive shaft. It is easy to mount stably without requiring the addition of a special fixing member.

  In the present invention, the clutch operating member is exposed to the operation pin that is operated around the rotation axis in the direction that passes through the work case portion and intersects the axis of the work drive shaft, and is exposed to the outside of the work case portion. An operation plate attached to a shaft end of the operation pin of the part, and the operation case member is provided with an operation guide member for positioning the operation plate in a direction along the rotation axis. Is preferred.

  With this configuration, it is possible to reliably regulate the slipping out of the work case without impairing the operability of the clutch operating member.

  In the present invention, it is preferable that the operation guide member includes a guide portion capable of allowing the operation plate to be operated around the rotation axis within a range corresponding to the on / off operation range of the work clutch. It is.

  By providing this configuration, it is possible to appropriately recognize the operation range by the clutch operation member using means for restricting the clutch operation member from coming out of the work case portion, and to improve operability with a simple structure. be able to.

  In the present invention, the work drive shaft includes an output transmission shaft that rotates integrally with the driven-side rotating member, and is fitted on the output transmission shaft so as to be rotatable relative to the output transmission shaft, and is better in the transmission direction than the output transmission shaft. And a cylindrical shaft body to which the power on the side is transmitted, and a portion of the cylindrical shaft body that is positioned closest to the upper side in the transmission direction is located in the main case portion. Inserted on the inner peripheral side of the cylindrical boss of the bevel gear, the inner peripheral side passage of the cylindrical shaft body at the position closest to the transmission direction is between the main case portion and the double shaft structure portion. It is preferable that they are connected.

  By providing this configuration, a double-shaft structure including the space on the inner peripheral side of the cylindrical boss of the output bevel gear in the main case portion, the inner peripheral side passage of the cylindrical shaft body, and the output transmission shaft body and the cylindrical shaft body The lubricating oil in the main case part can be guided to the work case part side by effectively using the part.

  In the present invention, the cylindrical shaft body is divided at a plurality of locations in the axial direction of the output transmission shaft body, and a member that rotates together with the cylindrical shaft body is attached to each of the divided cylindrical shaft bodies. It is preferable that

  By providing this configuration, even if an output transmission shaft body having a long axial length is used, appropriate lubrication can be performed by utilizing a gap between the cylindrical shaft bodies existing in the middle.

It is a left view of a riding type rice transplanter. It is a diagram which shows a power transmission system. It is an expanded sectional view of the main case part in a mission case. It is sectional drawing in the up-down direction of the case part between stocks in a mission case. It is sectional drawing in the horizontal direction of the branch case part in a mission case. It is a perspective view which shows the connection state of the stock case part and branch case part with respect to a main case part. It is explanatory drawing which shows the meshing part of the shift member and lower gear in an auxiliary transmission mechanism. It is a top view which shows the operating tool of a planting clutch. It is a disassembled perspective view which shows the operating tool of a planting clutch.

Hereinafter, an example of an embodiment of the present invention will be described based on the drawings.
In the description of the present embodiment, the front-rear direction and the left-right direction are described as follows unless otherwise specified. In other words, the forward traveling direction (see arrow F in FIGS. 1 and 2) during work travel of a working machine such as a riding rice transplanter to which the present invention is applied is “forward”, and the forward traveling direction (FIG. 1, FIG. 1). 2 (see arrow B in FIG. 2) is “rear”, the direction corresponding to the right side with reference to the forward posture in the front-rear direction (see arrow R in FIGS. 2 and 3) is “right”, and similarly the direction corresponding to the left side (see FIG. 2 (see arrow L in FIGS. 2 and 3) is “left”.

[Configuration of the entire work machine]
FIG. 1 shows a left side surface of a riding type rice transplanter as an example to which a working machine transmission device according to the present invention is applied.
This riding type rice transplanter includes a pair of left and right steering operations and driveable front wheels 11F, and a pair of left and right driveable rear wheels 11R as a travel drive device below the body frame 10, and is mounted on the body frame 10. The self-propelled traveling machine body 1 is provided in which the front wheels 11F and the rear wheels 11R are driven by receiving power from the engine E.

The traveling machine body 1 is provided with a driving unit 13 in which an engine E is installed on the driving unit floor 14 at the front of the machine body. On the driving unit floor 14 at the center in the front-rear direction of the traveling body 1 on the rear side of the driving unit 13, a boarding driving unit having a steering handle 15 and a driving seat 12 for steering the front wheels 11F is provided.
A fertilizer application device 9 (corresponding to a granular material supply device) is mounted on the rear portion of the driver seat 12. The fertilizer application device 9 feeds the fertilizer stored in the fertilizer tank 90 by a predetermined amount from a feeding device (not shown), sends the fertilizer to the grooving device 91 equipped in the seedling planting device 2 through a supply path (not shown), and supplies it to the field. Is configured to do. A seedling planting device 2 is supported on the rear side of the traveling machine body 1 through a link mechanism 25 having a hydraulic cylinder 26 for raising and lowering so as to be raised and lowered.
The riding type rice transplanter configured in this way performs planting work of seedlings such as rice on the field by the seedling planting device 2.

In the front part of the traveling machine body 1, preliminary seedling placing stands 17 are arranged on both the left and right sides of the prime mover 13 with a space in the left-right direction so as to be movable back and forth. The seedling planting device 2 is supported at the rear part of the traveling machine body 1 through a link mechanism 25 having a hydraulic cylinder 26 for raising and lowering so as to be raised and lowered.
The riding type rice transplanter configured in this way performs planting work of seedlings such as rice on the field by the seedling planting device 2.

  The seedling planting device 2 is configured in a four-row planting type, and includes a transmission case 21, a planting case 22 that is rotatably supported on the right and left lateral sides of the rear portion of the transmission case 21, and a planting case 22 includes a pair of planting arms 23 (planting claw drive mechanism) provided at both ends of the plant 22, a grounding float 24, and a seedling platform 20 on which a seedling is placed. As the seedling platform 20 is driven to reciprocate laterally to the left and right, the planting case 22 is rotationally driven so that the planting arms 23 alternately take out seedlings from the lower part of the seedling platform 20 and plant them on the rice field. It is configured.

A transmission case M that pivotally supports a front wheel 11F is connected and fixed to the front part of the body frame 10 in the traveling body 1, and an axle case 19 equipped with rear wheels 11R on the left and right is provided at the rear part of the body frame 10. It is supported. A front frame 10F extends forward from the mission case M, and an engine E is mounted sideways on the front frame 10F.
As shown in FIGS. 2 and 3, the left and right sides of the transmission case M are provided with axle cases 16 extending left and right and left and right front wheels 11 </ b> F and 11 </ b> F.
The axle case 19 of the rear wheel 11R is elastically supported below the pair of left and right front and rear frames 10A and 10A so as to be movable up and down separately through the suspension spring 18 so as to be able to perform a left and right rolling operation. .

[Power transmission system]
A power transmission structure in the transmission case M to which the power of the engine E is transmitted will be described.
The power of the engine E input to the mission case M includes a traveling drive system for driving the front wheels 11F, the rear wheels 11R and the like in the mission case M, and the seedling planting device 2 as a planting system working device or The output is branched and output to a working device drive system for driving a seeding device (not shown) and a fertilization drive system for driving the fertilizer application 9.

The transmission case M is branched from a main case portion 3 in which a sub-transmission mechanism 3A and the like of a traveling drive system is installed, and a stock case portion 4 (corresponding to a work case portion) disposed on the rear side of the main case portion 3. And a case portion 5.
The inter-case case unit 4 includes an inter-strain transmission mechanism 4A (corresponding to a work system transmission mechanism) that shifts and transmits the power output from the main case unit 3 to the seedling planting device 2, and the branch case unit 5 includes: A branch transmission mechanism 5 </ b> A that branches and transmits the power output from the main case portion 3 to the fertilizer application 9 is provided.

  The power of the engine E is transmitted to the pump shaft 60a of the hydrostatic continuously variable transmission 6 mounted on the outer wall of the main case 3 in the transmission case M, and from the motor shaft 61a of the hydrostatic continuously variable transmission 6. It is input to the inside of the case body 30 in the main case section 3. That is, the hydrostatic continuously variable transmission 6 is used as a continuously variable main transmission, and the power output from the main transmission is further shifted in the transmission case M.

[Travel drive system]
First, the transmission structure of the traveling drive system will be described.
As shown in FIG. 2, the power of the engine E is transmitted to a pump shaft 60 a that is a transmission input shaft of the hydrostatic continuously variable transmission 6 via a belt transmission mechanism 62, and the hydraulic pump 60 is rotationally driven. .
The motor shaft 61a, which is the speed change output shaft of the hydrostatic continuously variable transmission 6, is spline-fitted to the first speed change shaft 31 (corresponding to the upper side speed change shaft) in the case body 30 of the main case portion 3. The first transmission shaft 31 is driven to rotate as the motor 61 rotates.

As shown in FIG. 3, the first transmission shaft 31 is equipped with a traveling drive system upper-side low-speed gear 31a and upper-side high-speed gear 31b so as to rotate together, and the transmission transmission of the work device drive system is reduced. The output gear 31c is attached so as to rotate integrally.
The end of the first transmission shaft 31 opposite to the side connected to the motor shaft 61 a includes a shaft portion 33 a that penetrates the side wall 30 b of the case body 30 and protrudes to the outside of the case body 30. It is inserted into the cylindrical boss portion 33b of the extension shaft 33 and is pivotally supported so as to be relatively rotatable. The extension shaft 33 is provided with a planting transmission gear 33c on the outer peripheral portion of the cylindrical boss portion 33b. Has been.
The output gear 31c for reduction transmission and the planting transmission gear 33c are engaged with a relay gear 32f that is freely loosely fitted to a second transmission shaft 32 described later.

A second transmission shaft 32 (corresponding to a lower transmission shaft) having an axis parallel to the first transmission shaft 31 is pivotally supported by the case body 30. The second transmission shaft 32 includes a lower-side low-speed gear 32a (corresponding to the lower-side gear) that meshes with the upper-side low-speed gear 31a, and a lower-side high-speed gear 32b (which corresponds to the lower-side gear) that meshes with the upper-side high-speed gear 31b. Is supported on the second speed change shaft 32 so as to be relatively rotatable.
The gear pair of the upper side low speed gear 31a and the lower side low speed gear 32a, the gear pair of the upper side high speed gear 31b and the lower side high speed gear 32b, and the second transmission shaft 32 between these gear pairs. The auxiliary transmission mechanism 3A is configured by including a shift member 34 pivotally supported on the auxiliary transmission mechanism 34.
Of the gear pairs, the combination of the upper-side low-speed gear 31a and the lower-side low-speed gear 32a is a low-speed gear pair suitable for work traveling, and the combination of the upper-side high-speed gear 31b and the lower-side high-speed gear 32b is on the road. High-speed gear pair suitable for running.

The shift member 34 is spline-fitted to the second transmission shaft 32 and is supported so as to be able to rotate integrally with the second transmission shaft 32 and to be slidable in the axial direction of the second transmission shaft 32. On both the left and right side surfaces of the shift member 34 facing the left and right gear pairs, there are a lower side low speed gear 32a and a lower side high speed gear 32b, which are located on the lower side in the power transmission direction of each gear pair. The meshing tooth portions 34a and 34b projecting in the left and right directions are provided.
Further, meshing recesses 32c that selectively mesh with the meshing teeth 34a and 34b of the shift member 34 in the lower-side low-speed gear 32a and the lower-side high-speed gear 32b at positions facing the shift member 34, respectively. , 32d are formed.

Of the meshing teeth 34 a and 34 b of the shift member 34, the meshing tooth 34 a on the side facing the lower-side low-speed gear 32 a having a large diameter is near the outer periphery of the shift member 34 and from the outer peripheral surface of the second transmission shaft 32. It is formed at a remote location. The meshing tooth portion 34b on the side facing the lower-side high speed gear 32b having a smaller diameter on the opposite side is formed near the inner peripheral edge of the shift member 34 and close to the outer peripheral surface of the second transmission shaft 32.
Of the meshing recesses 32c and 32d, the meshing recess 32c formed in the lower-side low-speed gear 32a has a shape that can mesh with the meshing tooth portion 34a on the shift member 34 side at a position opposite to the meshing recess 32c. It is formed at a location away from the outer peripheral surface of 32. Further, the meshing recess 32d formed in the lower-side high-speed gear 32b has a shape capable of meshing with the meshing tooth portion 34b on the shift member 34 side at a position opposite to the meshing recess 32d, and is close to the outer peripheral surface of the second transmission shaft 32. Is formed.

  As shown in FIG. 7, the meshing recess 32 d formed in the lower-side high-speed gear 32 b is formed in a shape communicating with the shaft support hole 32 e of the lower-side high-speed gear 32 b that is externally fitted to the second transmission shaft 32. Thus, the meshing recess 32d formed in the lower-side high speed gear 32b is formed close to the outer peripheral surface of the second transmission shaft 32 to the limit.

The shift member 34 can be operated from the outside of the case body 30 by using an operation plate 34c that supports the shift member 34 in a state of being held in, and an operation rod 34d fixed integrally with the operation plate 34c. It is configured.
The position where the operating rod 34d is pushed most into the case body 30 is the position where the shift member 34 has selected a low-speed gear pair suitable for work traveling, and the operating rod 34d is pulled most outward from the case body 30. The position is a position where the shift member 34 has selected a high-speed gear pair suitable for traveling on the road. A state where the shift member 34 exists at an intermediate position where no gear pair is selected is the neutral position.

The power transmitted to the second transmission shaft 32 via the shift member 34 is transmitted to the front wheel output gear 35b via the interlocking gear 35a fixed to the second transmission shaft 32. The front wheel output gear 35b is spline-fitted to the outer peripheral portion on the right end side of the cylindrical member 35c that is fitted on the front wheel drive shaft 63 so as to be relatively rotatable. The left end side of the cylindrical member 35c is connected to the differential case 70 through a boss portion of a rear wheel output bevel gear 35d that is spline-fitted to the outer peripheral portion so as to be integrally rotatable.
Therefore, when the front wheel output gear 35b is driven, the rear wheel output bevel gear 35d and the differential case 70 are rotationally driven via the cylindrical member 35c. As a result, the left and right front wheel drive shafts 63 are rotationally driven with the rotation of the differential case 70, and the rear wheel input bevel gear 64a and the rear wheel output shaft 64 (which are meshed with the rear wheel output bevel gear 35d) are rotated. (Corresponding to the traveling transmission shaft) is driven to rotate.

A diff-locking claw portion 71a is provided at the right end of the boss portion of the front wheel output gear 35b. A differential lock sliding claw portion 71b that can be engaged with and disengaged from the differential lock claw portion 71a is also formed at the left end portion of the sliding cylinder 71 that is externally fitted to the front wheel drive shaft 63. The differential claw sliding claw portion 71 b is engaged and disengaged by a rotation operation of a diff lock operation pin 72 provided through the case body 30. That is, the sliding cylinder 71 is moved along the axial direction of the front wheel drive shaft 63 by the rotation operation of the differential lock operation pin 72, and engages / disengages with respect to the differential lock claw portion 71a of the front wheel output gear 35b.
In the differential lock state in which the differential lock sliding claw portion 71b is engaged with the differential lock claw portion 71a, the differential by the differential device 7 is locked.

[Working equipment drive system]
A working device drive system that transmits power to the seedling planting device 2 of the planting work device will be described separately from the traveling drive system described above.
The power to the seedling planting device 2 is transmitted between the inter-case case section 4A and the planting clutch 8 (corresponding to a working clutch) in the inter-case case section 4 attached to the rear of the main case section 3. It is taken out from the output transmission shaft body 42 extended rearward from 4 and transmitted to the rear seedling planting device 2.

  As shown in FIGS. 4 and 6, the inter-case case portion 4 includes an inter-case case main body 40 configured separately from the case main body 30 of the main case portion 3. The inter-case case main body 40 is integrally connected and fixed to the main case portion 3 via a connecting bolt or the like (not shown). The inter-case case part 4 and the main case part 3 are connected in a state where the internal spaces communicate with each other in a sealed state in which the openings 40a and 30a formed at the connecting portions are joined together. ing.

Power transmission from the main case part 3 into the inter-case case part 4 includes a work system transmission shaft 37 provided over the left and right side walls 30b, 30b of the case body 30, a bevel gear 37a fixed to the work system transmission shaft 37, and its bevel gear. This is done via an output bevel gear 38 meshing with 37a.
The work system transmission shaft 37 is provided with a second external gear 36 b provided on the shaft portion of the work system transmission shaft 37 projecting outside the case body 30 on the shaft portion of the extension shaft 33 projecting outside the case body 30. The first external gear 36a is engaged with the first external gear 36a, thereby transmitting power.

In the inter-case case section 4, as shown in FIG. 4, a work drive shaft 41 (corresponding to a speed change operation shaft) that is long in the front-rear direction is disposed across the front and rear of the inter-case case section 4.
The work drive shaft 41 is externally fitted to the output transmission shaft body 42 to which the transmission shaft 27 to the rear seedling planting device 2 is coupled and the front end side portion of the output transmission shaft body 42 so as to be relatively rotatable, A double shaft structure is configured by a front cylindrical shaft body 43 (corresponding to a cylindrical shaft body) to which power on the upper side in the transmission direction is transmitted.

The front cylindrical shaft body 43 on the transmission upper side is located in a state where the front end portion has entered the inside of the case main body 30 of the main case portion 3. A spline portion is formed in a portion of the front cylindrical shaft body 43 located closest to the transmission direction, and the spline portion is located on the inner peripheral side of the cylindrical boss of the output bevel gear 38 located in the main case portion 3. Is inserted in the spline part.
The output bevel gear 38 is supported on the outer peripheral side of the boss part by a ball bearing 38a provided on the case body 30 side of the main case part 3, and thereby the front cylindrical shaft body 43 inserted on the inner peripheral side is also supported. .
The ball bearing 38a provided on the case body 30 side is fitted with a portion of the front cylindrical shaft body 43 having a slightly larger diameter on the rear side than the portion inserted into the output bevel gear 38. It is supported. Further, a larger-diameter portion of the front cylindrical shaft body 43 abuts on the rear end side of the inner race of the ball bearing 38a, thereby restricting the position to the front side.

  The front cylindrical shaft body 43 is formed with a small-diameter hole 43b communicating with the internal space of the main case portion 3 in front of the large-diameter hole 43a into which the output transmission shaft body 42 is inserted. The small diameter hole 43 b and the large diameter hole 43 a of the cylindrical shaft body 43 serve as an inner peripheral side passage that communicates the internal space of the main case portion 3 and the internal space of the inter-case case portion 4.

An intermediate cylindrical body 44 (corresponding to a cylindrical shaft body) and a rear cylindrical body 45 (cylinder) are provided on the outer peripheral portion of the output transmission shaft body 42 on the rear side of the portion where the front cylindrical shaft body 43 exists. (Corresponding to a shaft-like body) is externally fitted so as to be relatively rotatable.
A torque limiter 46 is provided between the rear end portion of the intermediate cylindrical body 44 and the front end portion of the rear cylindrical body 45.
A planting clutch 8 is provided between the rear end portion of the rear cylindrical body 45 and the output transmission shaft body 42 on the rear side of the rear cylindrical body 45.
Thus, the intermediate cylindrical body 44 and the rear cylindrical body 45 are externally fitted to the outer peripheral portion of the output transmission shaft body 42 so as to be relatively rotatable, and the output transmission shaft body 42 is connected to the front cylinder. Since it exists in the internal peripheral side channel | path of the shaft-shaped shaft body 43, it is easy to lubricate favorably in the inter-case case part 4. FIG.
That is, the lubricating oil existing in the internal space of the main case portion 3 flows through the inner peripheral side of the output bevel gear 38 through the cylindrical boss, and as shown by the broken arrow in FIG. On the work drive shaft 41 from between the intermediate cylindrical body 44, between the intermediate cylindrical body 44 and the rear cylindrical body 45, and between the rear cylindrical body 45 and the output transmission shaft body 42 on the rear side. Lubricating can be satisfactorily performed while utilizing the centrifugal force accompanying the rotation of the rotating member.

The front cylindrical shaft body 43 is formed with a spline portion 43c on the outer peripheral portion, and a shift gear 47 fitted on the spline portion 43c is equipped so as to be integrally rotatable and slidable.
The shift gear 47 includes a first tooth portion 47a and a second tooth portion 47b having a slightly different number of teeth and having an approximate diameter, and either one of the tooth portions 47a and 47b meshes with the driven gear 47c alternatively. As is possible, the position of the front cylindrical shaft body 43 can be changed along the axial direction.
As shown in FIG. 4, the movement range of the shift gear 47 is such that both the first tooth portion 47a and the second tooth portion 47b are located in the inter-case case portion 4, and the front portion of the first tooth portion 47a portion. Alternatively, the operation range by the inter-stock shift operation member 100 is set so that a part of the inter-stock shift operation member 100 can be switched to a state of protruding from the inter-case case part 4 and being located in the internal space of the main case part 3.

In the stock case 4, a transmission shaft 48 is provided that is positioned parallel to the work drive shaft 41. The driven gear 47c is provided on the transmission shaft 48 so as to be integrally rotatable.
The transmission shaft 48 is provided with a plurality (three in the figure) provided in constant engagement with a plurality of (three in the figure) transmission gears 44 a fixed to the intermediate cylindrical body 44 on the output transmission shaft body 42 side. The transmission gear 48a is provided in a loosely fitted state. The transmission gears 44a and 48a that are always meshed with each other, the transmission rod 48b that is slid within the transmission shaft 48, and the positioning mechanism 48c that uses a detent mechanism are used. The combination between them can be selected alternatively.

  The first transmission unit 4B that uses the shift gear 47 and the driven gear 47c, and the second transmission unit 4C that can selectively select a combination of the transmission gears 44a and 48a that are normally engaged. The inter-stock transmission mechanism 4A is configured.

The inter-company transmission operation member 100 in the inter-company transmission mechanism 4A is configured as shown in FIGS.
That is, the locking pin 102 that fits between the first tooth portion 47a and the second tooth portion 47b is fixed to the lower end portion of the operation shaft 101 that penetrates the upper wall portion of the inter-case case portion 4, and the upper wall A plate-like operating body 103 is provided at the upper end of the operating shaft 101 located outside the portion.
By rotating the plate-like operation body 103 around the axis of the operation shaft 101, the locking pin 102 existing in the eccentric position is configured to change the position of the shift gear 47 in the axial direction of the work drive shaft 41. Has been. The position of the plate-like operating body 103 around the axis is determined by the ball detent mechanism 104.

  The torque limiter 46 includes a receiving plate 46a fixed to the rear end of the intermediate cylindrical body 44, a pressing plate 46b that contacts the receiving plate 46a, and a pressing force applied toward the receiving plate 46a. And a coil spring 46c.

The planting clutch 8 is configured as follows.
Of the work drive shaft 41, the rear end portion of the rear cylindrical body 45 is engaged with the outer peripheral side spline of the rear cylindrical body 45 to rotate integrally with the rear cylindrical body 45. 80 is provided.
On the outer peripheral side of the output transmission shaft body 42 extending rearward from the rear cylindrical body 45, the spline portion 42 a formed on the outer peripheral surface of the output transmission shaft body 42 is engaged and output. A driven-side rotating member 81 is provided that can rotate integrally with the transmission shaft 42 and move in the axial direction of the output transmission shaft 42.
The driven-side rotating member 81 is pressed and urged toward the driving-side rotating member 80 by a pressing spring 82, and the opposing surfaces of the driving-side rotating member 80 and the driven-side rotating member 81 are mutually opposed. Engagement portions 80a and 81a capable of transmitting power in an engaged state are formed.

The pressing spring 82 is provided between a spring receiving portion 81b formed on the surface opposite to the side where the meshing portion 81a of the driven side rotating member 81 is formed and a fixed portion on the inner surface side of the inter-case case portion 4. It has been. As the fixed portion on the inner surface side of the inter-case case portion 4, the inner end portion of the inner race 49 a of the ball bearing 49 that supports the output transmission shaft body 42 is used, but this position is not necessarily required.
The shape of the pressing spring 82 is such that the winding diameter at the end of the work drive shaft 41 in contact with the spring receiving portion 81b in the axial direction is larger than the winding diameter of the side in contact with the inner end of the inner race 49a. It is formed into a large truncated cone shape.
Of this pressing spring 82, the winding diameter on the side in contact with the inner end portion of the inner race 49a is configured to be the same as or slightly larger than the outer diameter of the output transmission shaft body 42 fitted outside. Therefore, the position of the end portion can be positioned by using the inner end portion of the inner race 49a of the ball bearing 49 that supports the output transmission shaft body 42 without requiring any special positioning means.

As shown in FIG. 4, the driven-side rotating member 81 is operated to the side away from the driving-side rotating member 80 against the biasing force of the pressing spring 82 by a clutch operating member 83 that is in contact with the outer peripheral portion. And an engaging portion 81c with which the clutch operating member 83 is engaged is provided on the outer peripheral portion.
The clutch operation member 83 includes an operation pin 84 that penetrates the upper wall portion of the inter-case case portion 4. The lower end portion of the operation pin 84 abuts on the engagement portion 81 c of the driven side rotation member 81, and the operation pin 84. With the rotation operation, an operation portion 84a for moving the driven side rotation member 81 in the axial direction of the output transmission shaft body 42 is formed.

The clutch operating member 83 is a shaft end portion of the operation pin 84 at a portion exposed to the outside of the inter-case case portion 4 among the operation pins 84 operated around the rotation axis p <b> 1 in a direction intersecting the axis of the work drive shaft 41. Further, an operation plate 85 for rotating the operation pin 84 is attached. An operation guide member 86 that guides the rotation operation of the operation plate 85 about the rotation axis p <b> 1 while supporting a part of the operation plate 85 so as to be sandwiched between the upper and lower sides is provided on the outer side of the inter-case case portion 4. Is provided.
As a result, the position of the operation pin 84 in the direction along the rotation axis p <b> 1 is restricted by the operation plate 85, and the operation range around the rotation axis p <b> 1 is abutted between the operation plate 85 and the operation guide member 86. Regulated by.

The position of the spring receiving portion 81b of the driven-side rotating member 81 with respect to the engaging portion with the engaging portion 81c of the driven-side rotating member 81 at the lower end portion of the operation pin 84 is the radius of the driven-side rotating member 81. And in the axial direction of the work drive shaft 41, the position closer to the facing surface where the meshing portion 81 a is formed than the location where the driven rotation member 81 is engaged with the engagement portion 81 c. Is provided.
As described above, the spring receiving portion 81b is located on the inner side in the radial direction from the engagement portion between the operation pin 84 and the engagement portion 81c of the driven side rotation member 81, and on the side where the engagement portion 81a exists. The shape is greatly recessed so as to be close to each other. Thus, the axial length of the work drive shaft 41 of the pressing spring 82 can be prevented from being restricted by the position of the operation pin 84 in the axial direction of the work drive shaft 41, and the inter-case case portion 4 can be made compact. Can be planned.

[Fertilization drive system]
The fertilizer application drive system that branches and transmits the driving force to the fertilizer application device 9 from the traveling drive system described above is configured as follows.
As shown in FIG. 6, a branch case portion 5, which is configured separately from the main case portion 3, is connected and fixed to the rear side of the main case portion 3 via mounting bolts (not shown). ing.
The main case part 3 and the branch case part 5 communicate with each other in a sealed state in which the openings 30a and 50a formed at the connecting portions are joined to each other.

As shown in FIG. 5, the branch case portion 5 has an input side tubular portion 50 </ b> A that supports the rear wheel output shaft 64 that extends rearward from the main case portion 3 and a direction that intersects the rear wheel output shaft 64. An output side tubular portion 50B that is externally fitted to the extended branch transmission shaft 51 and supports the branch transmission shaft 51 is provided. The input-side cylindrical portion 50A and the output-side cylindrical portion 50B are configured as a single body having a common internal space.
A branch output bevel gear 52 that transmits power from the rear wheel output shaft 64 to the branch transmission shaft 51 is provided in the input side tubular portion 50A, and a fertilizer bevel gear 53 (branch input bevel gear 53) that meshes with the branch output bevel gear 52. Is provided in the output-side cylindrical portion 50B.
The branch output bevel gear 52 is provided in the input side cylindrical portion 50 </ b> A closer to the main case portion 3 than the branch transmission shaft 51.

A rear wheel output shaft 64 having a front wheel input bevel gear 64a meshing with the rear wheel output bevel gear 35d at the front end is supported by a ball bearing 39 provided on the case body 30 of the main case 3 on the front end side. The end portion is supported by a ball bearing 54 provided near the rear end portion of the branch case portion 5.
The rear wheel output shaft 64 is provided with a stepped portion 64C (corresponding to a positioning portion) at an intermediate position in the axial direction, and the front portion corresponding to the upper side in the transmission direction is larger in diameter than the stepped portion 64C. In the shaft portion 64A, a rear side corresponding to the lower side in the transmission direction than the stepped portion 64C is formed in the small-diameter shaft portion 64B.
The step portion 64C is formed near the boundary between the main case portion 3 and the branch case portion 5, and a spline portion 64D is formed in a portion near the step portion 64C in the small-diameter shaft portion 64B. The spline portion 64D is branched to the spline portion 64D. The output bevel gear 52 is spline-fitted.

An opening 50 a of the branch case portion 5 formed at a location facing the main case portion 3 has an inner diameter through which the branch output bevel gear 52 supported by the rear wheel output shaft 64 can be inserted.
Therefore, when the rear wheel output shaft 64 is assembled into the branch case portion 5, it can be incorporated into the branch case portion 5 in a state where the branch output bevel gear 52 is previously supported on the rear wheel output shaft 64. Convenience can be achieved.

A branch transmission shaft 51 equipped with a fertilization bevel gear 53 that meshes with a branch output bevel gear 52 supported by the rear wheel output shaft 64 at the input side end is arranged in a posture orthogonal to the rear wheel output shaft 64. ing. And it is comprised so that an input side edge part can be inserted / extracted from the output side opening 50b side formed in the output side cylindrical part 50B of the branch case part 5, and the output side edge part is the output side opening 50b of the output side cylindrical part 50B. It is supported in a state protruding from the outside.
An unillustrated interlocking shaft to the fertilizer application device 9 is connected to the projecting portion of the branch transmission shaft 51 projecting outward from the output side opening 50b.

  Further, the branch transmission shaft 51 is a portion corresponding to the insertion limit position to the output side tubular portion 50 </ b> B, and the input side end abuts against the rear wheel output shaft 64. That is, when the branch transmission shaft 51 is inserted into the output-side tubular portion 50B from the output-side opening 50b until reaching the insertion limit position, the input-side end portion is in such a positional relationship that it abuts against the rear-wheel output shaft 64. The position of the rear wheel output shaft 64 with respect to the side tubular portion 50A is determined.

  The fertilization bevel gear 53 is supported so as to be rotatable relative to the branch transmission shaft 51, and the branch transmission shaft 51 and the fertilization bevel gear 53 can be freely engaged and disengaged via a fertilization clutch 55 (corresponding to a work clutch). It is configured.

The fertilization clutch 55 includes a cylindrical shift member 56 that is spline-fitted to a spline portion formed on the outer peripheral surface of the branch transmission shaft 51. Then, by engaging / disengaging the claw portion 56a formed on the surface of the cylindrical shift member 56 facing the fertilizer bevel gear 53 and the engaging recess 53a on the fertilizer bevel gear 53 side facing the cylindrical shift member 56. The fertilization bevel gear 53 is configured to be switchable between a state where the rotation of the bevel gear 53 is transmitted to the branch transmission shaft 51 and a state where the transmission is cut off.
The cylindrical shift member 56 is pressed and biased toward the fertilizer bevel gear 53 by a coil spring 57, and a clutch operating shaft that operates the cylindrical shift member 56 toward the side away from the fertilizer bevel gear 53 against this pressing bias force. A body 58 is provided so as to penetrate the output-side cylindrical portion 50B.

[Other Embodiment 1]
In said embodiment, although the inter-case case part 4 was shown as a work case part, it is not restricted to this. For example, when the working machine is used for a seeder equipped with a direct seeding device, the work case unit becomes a work case unit for changing the seeding interval by the direct seeding device.
Other configurations may be the same as those in the above-described embodiment.

[Second embodiment]
In said embodiment, although the fertilizer application apparatus 9 is used as a granular material supply apparatus, it is not restricted to this.
For example, a medicine such as a herbicide or a pest repellent may be supplied.
Other configurations may be the same as those in the above-described embodiment.

[3 of another embodiment]
In the above embodiment, the technique applied to the planting clutch 8 as a working clutch is shown, but the present invention is not limited to this. For example, although not illustrated, the fertilization clutch 55 may be configured in the same structure as the planting clutch 8 as the above-described working clutch.
Other configurations may be the same as those in the above-described embodiment.

[4 of another embodiment]
In the above embodiment, as the cylindrical shaft body, the front cylindrical shaft body 43, the intermediate cylindrical body 44, and the rear cylindrical body 45 are exemplified as a structure having three structures. The structure is not limited to this.
For example, a structure using only the front cylindrical shaft body 43 as the cylindrical shaft body or a structure using a combination of more cylindrical bodies may be used.
Other configurations may be the same as those in the above-described embodiment.

  The present invention is not limited to a riding type rice transplanter for four-row planting. It can be applied to a work machine transmission.

1 traveling machine body 2 seedling planting device (working device)
3 Main case part 3A Sub transmission mechanism 4A Work system transmission mechanism 4 Seeding case part (work case part)
5 branch case part 5A branch transmission mechanism 8 work clutch 41 speed change operation shaft (work drive shaft)
42 Output transmission shaft body 43 Cylindrical shaft body 47 Shift gear 50A Input side cylindrical portion 50B Output side cylindrical portion 51 Branch drive shaft 64 Driving shaft 64C Positioning portion 80 Drive side rotating member
80a Engagement part 81 Driven side rotation member 81a Engagement part 81b Spring receiving part 81c Engagement part 82 Pressing spring 83 Clutch operation member 84 Operation pin 85 Operation plate 86 Operation guide member p1 Rotation shaft center

Claims (8)

A main case portion that includes a speed change mechanism for shifting the input engine power and outputs speed change power to the travel drive system;
A working system transmission mechanism that shifts engine power input through the main case section, and a work case section that outputs shifting power to a working device; and
The work case portion includes a work drive shaft that transmits the shift power from the work system transmission mechanism to the work device, and a work clutch that can intermittently transmit power from the work system transmission mechanism to the work drive shaft. Decorated,
The work clutch includes a drive-side rotating member to which power from the work-system transmission mechanism is transmitted on the upper side in the power transmission direction, and the work drive shaft on the lower side in the power transmission direction than the drive-side rotating member. And a driven side rotating member supported so as to be integrally rotatable with the work drive shaft,
The driving-side rotating member and the driven-side rotating member are formed with meshing portions capable of transmitting power in a meshed state on the respective opposing surfaces, and the driven-side rotating member with respect to the driving-side rotating member The rotating member is configured to be movable along the axial direction of the work drive shaft,
A pressing spring that presses and biases the driven-side rotating member toward the driving-side rotating member is provided to be fitted on the work drive shaft, and the driven-side rotating member is resisted against the biasing force of the pressing spring. A clutch operating member operable to the side away from the driving side rotating member is provided,
The clutch operating member is configured to engage with an engaging portion formed on the outer peripheral side of the driven side rotating member and to operate the driven side rotating member away from the driving side rotating member,
The transmission device for a working machine, wherein the pressing spring is provided on an inner side in the radial direction of the driven side rotation member with respect to an engagement portion between the clutch operation member and the engagement portion.   A spring receiving portion is formed on a surface opposite to the side on which the meshing portion of the driven side rotating member is formed, and the spring receiving portion is engaged with the clutch operation member in the axial direction of the work drive shaft. The transmission device for a working machine according to claim 1, wherein the transmission device is provided at a position closer to the facing surface where the meshing portion is formed than an engagement position with a portion.   The pressing spring is mounted between the spring receiving portion and the fixed portion on the inner surface side of the work case portion, and has a larger winding diameter on the other end side than the one end side in the axial direction of the work drive shaft. The transmission device for a working machine according to claim 2, wherein the transmission device is formed in a trapezoidal shape.   The pressing spring is formed such that a winding diameter on a side supported by the spring receiving portion of the driven side rotation member is larger than a winding diameter on the opposite side, and the winding diameter on the opposite side is the pressing spring. The transmission device for a working machine according to claim 3, wherein the inner peripheral surface is set to a degree in contact with the outer peripheral surface of the work drive shaft. The clutch operating member includes an operation pin that is operated around a rotation axis in a direction that passes through the work case portion and intersects the axis of the work drive shaft, and the operation pin that is exposed to the outside of the work case portion. An operation plate attached to the shaft end of
The transmission device for a working machine according to any one of claims 1 to 4, wherein an operation guide member that positions the operation plate in a direction along the rotation axis of the operation plate is provided in the work case unit.   6. The work machine according to claim 5, wherein the operation guide member includes a guide portion that allows operation of the operation plate around the rotation axis within a range corresponding to an operation range of the work clutch. Transmission device. The work drive shaft is externally fitted to the output transmission shaft body so as to be rotatable relative to the output transmission shaft body so as to rotate integrally with the driven side rotation member, and power on the upper side in the transmission direction is transmitted to the output transmission shaft body. A cylindrical shaft body, and a double shaft structure portion by,
Of the cylindrical shaft body, a portion located closest to the transmission direction is inserted into the cylindrical boss inner peripheral side of the output bevel gear located in the main case portion, and the portion located closest to the transmission direction The transmission device of the working machine according to any one of claims 1 to 6, wherein an inner peripheral side passage of the cylindrical shaft body connects between the main case portion and the double shaft structure portion.   The cylindrical shaft body is divided at a plurality of locations in the axial direction of the output transmission shaft body, and a member that rotates together with the cylindrical shaft body is attached to each of the divided cylindrical shaft bodies. 7. A power transmission device for a working machine according to 7.

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