JP2016136902A - Agriculture feeder - Google Patents

Abstract

PROBLEM TO BE SOLVED: To avoid a fear that a feed amount from an agricultural feeder is different for individual feeders, due to the backlash which may occur between a drive shaft and a one-way clutch.SOLUTION: An agriculture feeder comprises one-way clutches 71 to 73 for transmitting a power from a vehicle body 1 to a drive shaft 48. The drive shaft 48 is constituted of a square shaft having a polygonal cross section. The one-way clutches 71 to 73 include inner rings 71C to 73C to be fitted on the drive shaft 48. A cylindrical body 110 made of a resin is press-fitted between the drive shaft 48 and the inner rings 71C to 73C.SELECTED DRAWING: Figure 19

Description

  The present invention relates to an agricultural supply apparatus including a one-way clutch that transmits power from a traveling vehicle body to a drive shaft.

  In a fertilizer application which is an example of an agricultural supply device, power from a traveling vehicle body is transmitted to a drive shaft having a hexagonal cross section provided in the fertilizer application device through two one-way clutches externally fitted to the drive shaft. (For example, refer patent document 1).

JP 2002-95312 (paragraph numbers 0039 to 0044, FIG. 4, FIG. 7, FIG. 13, FIG. 14)

  In the above configuration, since the cross-section of the drive shaft is hexagonal, each one-way clutch has a hexagonal fitting hole that is the same as the cross-sectional shape of the drive shaft on the inner ring of the one-way clutch that is externally fitted to the drive shaft. Yes. In such a case, the drive shaft and the one-way clutch have individual differences due to their respective manufacturing errors, and due to these individual differences, there is a backlash that differs for each agricultural supply device between the drive shaft and the inner ring of the one-way clutch. May occur. Then, when rattling occurs between the drive shaft and the inner ring of the one-way clutch, the greater the rattling, the greater the transmission loss that occurs between the driving shaft and the one-way clutch. Therefore, in an agricultural supply device including such a drive shaft and a one-way clutch, the power from the traveling vehicle body is the same due to rattling between the drive shaft and the inner ring of the one-way clutch that are different for each agricultural supply device. Even if it exists, there exists a possibility that a difference may arise in the rotation speed of the drive shaft obtained via a one-way clutch. As a result, there is a possibility that the supply amount from the agricultural supply device may cause a problem that differs depending on the agricultural supply device.

  An object of the present invention is to avoid a possibility that a supply amount from an agricultural supply device is different from one agricultural supply device to another due to rattling generated between a drive shaft and an inner ring of a one-way clutch.

In the problem solving means of the present invention,
With a one-way clutch that transmits the power from the traveling vehicle body to the drive shaft,
The drive shaft is constituted by an angular axis having a polygonal cross section,
The one-way clutch includes an inner ring that is externally fitted to the drive shaft,
A resin cylindrical body is press-fitted between the drive shaft and the inner ring.

  According to this means, since the resin cylindrical body is press-fitted between the drive shaft and the inner ring of the one-way clutch, the drive shaft and the one-way clutch may be caused by individual differences between the drive shaft and the one-way clutch. A backlash between the inner ring and the inner ring can be eliminated, and a transmission loss between the drive shaft and the one-way clutch caused by the backlash can be eliminated.

  As a result, the rotation of the drive shaft obtained through the one-way clutch for each agricultural supply device due to the transmission loss generated between the drive shaft and the one-way clutch even though the power from the traveling vehicle body is the same. It is possible to avoid the possibility that the number is different.

  As a result, it is possible to avoid the possibility that the supply amount from the agricultural supply device may be different for each agricultural supply device.

In another problem solving means of the present invention,
With a one-way clutch that transmits the power from the traveling vehicle body to the drive shaft,
The drive shaft is constituted by an angular axis having a polygonal cross section,
The one-way clutch includes an inner ring that is externally fitted to the drive shaft,
Press-fit a resin cylindrical body between the drive shaft and the inner ring,
The cylindrical body is formed in a cylindrical shape by a plurality of bending members.

  According to this means, since the resin cylindrical body is press-fitted between the drive shaft and the inner ring of the one-way clutch, the drive shaft and the one-way clutch may be caused by individual differences between the drive shaft and the one-way clutch. A backlash between the inner ring and the inner ring can be eliminated, and a transmission loss between the drive shaft and the one-way clutch caused by the backlash can be eliminated.

  As a result, the rotation of the drive shaft obtained through the one-way clutch for each agricultural supply device due to the transmission loss generated between the drive shaft and the one-way clutch even though the power from the traveling vehicle body is the same. It is possible to avoid the possibility that the number is different.

  As a result, it is possible to avoid the possibility that the supply amount from the agricultural supply device may be different for each agricultural supply device.

  By the way, for example, when the cylindrical body is composed of a single cylindrical member, when the cylindrical body is press-fitted between the drive shaft and the inner ring of the one-way clutch, the cylindrical body is fitted on one end of the drive shaft. After that, it is necessary to slide the cylindrical body from one end of the drive shaft to the press-fitting location. Therefore, it takes time to press-fit the cylindrical body between the drive shaft and the inner ring of the one-way clutch. Further, during the sliding movement of the cylindrical body, the inner peripheral surface of the cylindrical body may be damaged due to sliding contact with the corners of the drive shaft.

  On the other hand, in this means, since the cylindrical body is constituted by a plurality of curved members, the cylindrical bodies are formed by press-fitting each curved member between the drive shaft and the inner ring of the one-way clutch. The tubular body is placed between the drive shaft and the inner ring of the one-way clutch without the need to fit around one end of the drive shaft or to slide the tubular body from one end of the drive shaft to the press-fitting location. Can be press-fitted.

  In addition, since it is not necessary to slide the cylindrical body while it is fitted on the drive shaft, the inner peripheral surface of the cylindrical body is in sliding contact with the corners of the drive shaft during the sliding movement of the cylindrical body. It is possible to avoid the possibility of being damaged due to this.

In another problem solving means of the present invention,
With a one-way clutch that transmits the power from the traveling vehicle body to the drive shaft,
The drive shaft is constituted by an angular axis having a polygonal cross section,
The one-way clutch includes an inner ring that is externally fitted to the drive shaft,
The inner ring includes a small-diameter portion having a polygonal fitting hole that is the same as the cross-section of the drive shaft, and an enlarged-diameter portion having a round hole larger in diameter than a circumscribed circle of the drive shaft,
A cylindrical body made of resin is press-fitted between the drive shaft and the enlarged diameter portion.

  According to this means, since the resin cylindrical body is press-fitted between the drive shaft and the enlarged diameter portion of the inner ring, the drive shaft and the one-way clutch may be caused due to individual differences between the drive shaft and the one-way clutch. The backlash between the inner ring and the inner ring can be eliminated, and the transmission loss between the drive shaft and the one-way clutch caused by the backlash can be eliminated.

  As a result, the rotation of the drive shaft obtained through the one-way clutch for each agricultural supply device due to the transmission loss generated between the drive shaft and the one-way clutch even though the power from the traveling vehicle body is the same. It is possible to avoid the possibility that the number is different.

  As a result, it is possible to avoid the possibility that the supply amount from the agricultural supply device may be different for each agricultural supply device.

  In addition, by providing the inner ring of the one-way clutch with the aforementioned small diameter portion and enlarged diameter portion, for example, the entire inner ring is enlarged in diameter, and the entire length of the inner ring is between the drive shaft and the inner ring of the one-way clutch. Compared with the case where a cylindrical body having a pressure is press-fitted, the one-way clutch can be prevented from being enlarged in the radial direction.

  Moreover, the contact area between the inner ring of the one-way clutch and the cylindrical body can be increased by press-fitting the cylindrical body between the drive shaft and the enlarged diameter portion of the inner ring. As a result, the occurrence of slippage between the inner ring of the one-way clutch and the cylindrical body can be effectively suppressed, and transmission loss caused by the slip between the inner ring of the one-way clutch and the cylindrical body can be generated. Can be effectively suppressed.

In another problem solving means of the present invention,
With a one-way clutch that transmits the power from the traveling vehicle body to the drive shaft,
The drive shaft is constituted by an angular axis having a polygonal cross section,
The one-way clutch includes an inner ring that is externally fitted to the drive shaft,
The inner ring includes a small-diameter portion having a polygonal fitting hole that is the same as the cross-section of the drive shaft, and an enlarged-diameter portion having a round hole larger in diameter than a circumscribed circle of the drive shaft,
Press-fit a resin cylindrical body between the drive shaft and the enlarged diameter portion,
The cylindrical body is formed in a cylindrical shape by a plurality of bending members.

  According to this means, since the resin cylindrical body is press-fitted between the drive shaft and the enlarged diameter portion of the inner ring, the drive shaft and the one-way clutch may be caused due to individual differences between the drive shaft and the one-way clutch. The backlash between the inner ring and the inner ring can be eliminated, and the transmission loss between the drive shaft and the one-way clutch caused by the backlash can be eliminated.

  As a result, the rotation of the drive shaft obtained through the one-way clutch for each agricultural supply device due to the transmission loss generated between the drive shaft and the one-way clutch even though the power from the traveling vehicle body is the same. It is possible to avoid the possibility that the number is different.

  As a result, it is possible to avoid the possibility that the supply amount from the agricultural supply device may be different for each agricultural supply device.

  In addition, by providing the inner ring of the one-way clutch with the aforementioned small diameter portion and enlarged diameter portion, for example, the entire inner ring is enlarged in diameter, and the entire length of the inner ring is between the drive shaft and the inner ring of the one-way clutch. Compared with the case where a cylindrical body having a pressure is press-fitted, the one-way clutch can be prevented from being enlarged in the radial direction.

  Moreover, the contact area between the inner ring of the one-way clutch and the cylindrical body can be increased by press-fitting the cylindrical body between the drive shaft and the enlarged diameter portion of the inner ring. As a result, the occurrence of slippage between the inner ring of the one-way clutch and the cylindrical body can be effectively suppressed, and transmission loss caused by the slip between the inner ring of the one-way clutch and the cylindrical body can be generated. Can be effectively suppressed.

  By the way, for example, when the cylindrical body is constituted by a single cylindrical member, when the cylindrical body is press-fitted between the drive shaft and the enlarged diameter portion of the inner ring, the cylindrical body is attached to one end of the drive shaft. After the fitting, it is necessary to slide the cylindrical body from one end of the drive shaft to the press-fitting location. Therefore, it takes time to press-fit the cylindrical body between the drive shaft and the inner ring of the one-way clutch. Further, during the sliding movement of the cylindrical body, the inner peripheral surface of the cylindrical body may be damaged due to sliding contact with the corners of the drive shaft.

  On the other hand, in this means, since the cylindrical body is constituted by a plurality of curved members, each curved member is press-fitted between the drive shaft and the enlarged diameter portion of the inner ring, thereby the cylindrical body. Between the drive shaft and the diameter-enlarged portion of the inner ring without requiring the effort of externally fitting the cylinder to one end of the drive shaft and the effort of sliding the cylindrical body from one end of the drive shaft to the press-fitting location. It can be pressed in between.

  In addition, since it is not necessary to slide the cylindrical body while it is fitted on the drive shaft, the inner peripheral surface of the cylindrical body is in sliding contact with the corners of the drive shaft during the sliding movement of the cylindrical body. It is possible to avoid the possibility of being damaged due to this.

As one of the means for making the present invention more suitable,
The inner periphery of the cylindrical body is formed in the same polygon as the cross-sectional shape of the drive shaft so as to be in surface contact with the outer peripheral surface of the drive shaft,
A plurality of ridges extending in the axial direction of the drive shaft at a position deviating from a portion facing the corner of the drive shaft on the outer peripheral surface of the cylindrical body;
In the press-fitted state of the cylindrical body, each of the protrusions is in pressure contact with the inner peripheral surface of the inner ring, and the inner peripheral surface of the cylindrical body is in press contact with the outer peripheral surface of the drive shaft.

  According to this means, since the outer peripheral surface of the cylindrical body is provided with a plurality of protrusions extending in the axial direction of the drive shaft, it is easy to press-fit the cylindrical body between the drive shaft and the inner ring of the one-way clutch. Become. When the cylindrical body is press-fitted between the drive shaft and the inner ring of the one-way clutch, the inner peripheral surface of the cylindrical body is formed as each protrusion of the cylindrical body presses against the inner peripheral surface of the inner ring. The plurality of flat portions to be pushed out to the drive shaft side come into close contact with the plurality of flat portions forming the outer peripheral surface of the drive shaft.

  As a result, while making it easy to press-fit the cylindrical body between the drive shaft and the inner ring of the one-way clutch, the drive shaft and the inner ring of the one-way clutch may be caused by individual differences between the drive shaft and the one-way clutch. It is possible to more reliably eliminate rattling between the two.

As one of the means for making the present invention more suitable,
The inner periphery of the cylindrical body is formed in the same polygon as the cross-sectional shape of the drive shaft so as to be in surface contact with the outer peripheral surface of the drive shaft,
A plurality of ridges extending in the axial direction of the drive shaft at a position deviating from a portion facing the corner of the drive shaft on the outer peripheral surface of the cylindrical body;
In the press-fitted state of the cylindrical body, each of the protrusions presses against the inner peripheral surface of the inner ring, and the inner peripheral surface of the cylindrical body presses against the outer peripheral surface of the drive shaft,
Each of the protrusions is inclined at both ends in a state where the outward protrusion amount decreases toward both ends in the axial direction.

  According to this means, since the outer peripheral surface of the cylindrical body is provided with a plurality of protrusions extending in the axial direction of the drive shaft, it is easy to press-fit the cylindrical body between the drive shaft and the inner ring of the one-way clutch. Become. When the cylindrical body is press-fitted between the drive shaft and the inner ring of the one-way clutch, the inner peripheral surface of the cylindrical body is formed as each protrusion of the cylindrical body presses against the inner peripheral surface of the inner ring. The plurality of flat portions to be pushed out to the drive shaft side come into close contact with the plurality of flat portions forming the outer peripheral surface of the drive shaft.

  In addition, each protrusion of the cylindrical body is inclined at both ends in a state where both ends in the axial direction are less outwardly projected, so that the gap between the drive shaft and the inner ring of the one-way clutch is reduced. When the cylindrical body is press-fitted into the cylinder, it is possible to make it easier to press-fit the cylindrical body between the drive shaft and the inner ring of the one-way clutch regardless of the direction of the cylindrical body.

  As a result, the inner ring of the drive shaft and the one-way clutch may be generated due to individual differences between the drive shaft and the one-way clutch while facilitating the press-fitting of the cylindrical body between the drive shaft and the inner ring of the one-way clutch. Can be more reliably resolved.

As one of the means for making the present invention more suitable,
Provided with a plurality of protrusions extending in the axial direction of the drive shaft on the inner peripheral surface of the cylindrical body,
The outer periphery of the cylindrical body is formed in the same shape as the inner periphery of the inner ring so as to be in surface contact with the inner peripheral surface of the inner ring,
In the press-fitted state of the cylindrical body, each of the protrusions is in pressure contact with the outer peripheral surface of the drive shaft, and the outer peripheral surface of the cylindrical body is press-contacted with the inner peripheral surface of the inner ring.

  According to this means, since the plurality of protrusions extending in the axial direction of the drive shaft are provided on the inner peripheral surface of the cylindrical body, the cylindrical body is press-fitted between the drive shaft and the inner ring of the one-way clutch. It becomes easy. Then, when the cylindrical body is press-fitted between the drive shaft and the inner ring of the one-way clutch, the outer peripheral surface of the cylindrical body is brought into contact with the outer peripheral surface of the drive shaft as the protrusions of the cylindrical body press against the outer peripheral surface of the drive shaft. It is pushed out to the inner ring side of the clutch and comes into close contact with the inner peripheral surface of the inner ring.

  As a result, while making it easy to press-fit the cylindrical body between the drive shaft and the inner ring of the one-way clutch, the drive shaft and the inner ring of the one-way clutch may be caused by individual differences between the drive shaft and the one-way clutch. It is possible to more reliably eliminate rattling between the two.

As one of the means for making the present invention more suitable,
Provided with a plurality of protrusions extending in the axial direction of the drive shaft on the inner peripheral surface of the cylindrical body,
The outer periphery of the cylindrical body is formed in the same shape as the inner periphery of the inner ring so as to be in surface contact with the inner peripheral surface of the inner ring,
In the press-fitted state of the cylindrical body, each of the protrusions presses against the outer peripheral surface of the drive shaft, and the outer peripheral surface of the cylindrical body presses against the inner peripheral surface of the inner ring,
Each of the protrusions is inclined at both ends in a state where the outward protrusion amount decreases toward both ends in the axial direction.

  According to this means, since the plurality of protrusions extending in the axial direction of the drive shaft are provided on the inner peripheral surface of the cylindrical body, the cylindrical body is press-fitted between the drive shaft and the inner ring of the one-way clutch. It becomes easy. Then, when the cylindrical body is press-fitted between the drive shaft and the inner ring of the one-way clutch, the outer peripheral surface of the cylindrical body is brought into contact with the outer peripheral surface of the drive shaft as the protrusions of the cylindrical body press against the outer peripheral surface of the drive shaft. It is pushed out to the inner ring side of the clutch and comes into close contact with the inner peripheral surface of the inner ring.

  In addition, each end of the cylindrical body is inclined with both ends being inclined toward the both ends in the axial direction of the drive shaft so that the amount of outward protrusion is reduced. When the cylindrical body is press-fitted between the two, the cylindrical body can be more easily press-fitted between the drive shaft and the inner ring of the one-way clutch regardless of the direction of the cylindrical body.

  As a result, the inner ring of the drive shaft and the one-way clutch may be generated due to individual differences between the drive shaft and the one-way clutch while facilitating the press-fitting of the cylindrical body between the drive shaft and the inner ring of the one-way clutch. Can be more reliably resolved.

As one of the means for making the present invention more suitable,
The drive shaft is a hexagonal shaft having a hexagonal cross section,
The cylindrical body is formed into a cylindrical shape by two curved members arranged in a state of sandwiching two opposite corners of the hexagonal shaft,
Each of the bending members includes an inner surface composed of three plane portions that are in surface contact with the outer peripheral surface of the drive shaft.

  According to this means, since the three plane portions forming the inner surface of each bending member have an included angle of 120 degrees, each bending member has a draft of 30 degrees on the inner surface thereof. Thereby, it is possible to facilitate die cutting after molding each bending member without providing a dedicated draft on the inner surface of each bending member.

  For example, as compared with the case where the cylindrical body is constituted by three curved members, it is possible to facilitate the assembly by reducing the number of parts.

  Therefore, it is possible to improve the assemblability of the cylindrical body while facilitating the molding of each bending member.

It is a left view of a riding rice transplanter. It is a top view of a riding rice transplanter. It is a vertical left side view of the rear upper part of the traveling vehicle body showing a transmission configuration from the traveling vehicle body to the fertilizer application. It is a front view of the fertilizer application which shows the composition of a fertilizer application. It is a cross-sectional top view of the fertilizer applicator which shows the transmission structure from a traveling vehicle body to a fertilizer applicator, etc. It is a rear view of the fertilizer application which shows the power transmission composition from a running body to a fertilizer application. It is a vertical left side view of the rear upper part of the traveling vehicle body showing the configuration of the fertilizer application. It is a top view of the principal part which shows the drive structure etc. of a fertilizer application. It is a cross-sectional top view of the right end part of the fertilizer applicator which shows the transmission structure to the drive shaft, etc. of a fertilizer applicator. It is a front view of the right end part of a fertilizer application which shows the power transmission composition to the drive shaft of a fertilizer applicator. It is a partial vertical section right side view of a fertilizer applicator showing the transmission composition to the drive shaft of the fertilizer applicator. It is a vertical front view of the right end part of the fertilizer application which shows the power transmission composition to the drive shaft of a fertilizer applicator. It is a cross-sectional top view of the principal part which shows the transmission structure to the drive shaft of a fertilizer applicator. It is a vertical right side view of the principal part showing a state before the second arm is forwardly swung (after reverse rocking) in a state where the linkage arm is operated to the position where the feeding amount is maximum in the standard fertilization state. It is a vertical right side view of the principal part showing a state before the second arm is back-swinged (after forward-swinging) in a state where the linkage arm is operated to the position where the feeding amount is maximum in the standard fertilization state. It is a vertical right side view of the transmission mechanism for feeding showing a state before the second arm is forwardly swung (after backward rocking) in a state in which the linkage arm is operated to the minimum amount of feeding amount in the standard fertilization state. FIG. 10 is a vertical right side view of the feeding transmission mechanism showing a state before the second arm is back rocked (after forward rocking) in a state where the linkage arm is operated to the minimum feeding amount position in the standard fertilization state. It is a vertical right side view of the transmission mechanism for feeding showing the state switched to the reduced weight fertilization state. FIG. 5 is a cross-sectional plan view around the right end of the drive shaft showing a structure in which a cylindrical body is press-fitted between the drive shaft and the inner ring of each one-way clutch. It is a vertical side view around the right end of the drive shaft showing a structure in which a cylindrical body is press-fitted between the drive shaft and the inner ring of each one-way clutch. It is a side view of the cylindrical body which shows the structure of a cylindrical body. It is a vertical front view of the cylindrical body which shows the structure of a cylindrical body. It is a vertical side view around the right end portion of the drive shaft showing the configuration of the cylindrical body exemplified in another embodiment [7]. It is a side view of the cylindrical body which shows the structure of the cylindrical body illustrated in another embodiment [7]. It is a vertical front view of the cylindrical body which shows the structure of the cylindrical body illustrated in another embodiment [7]. It is a vertical side view around the right end portion of the drive shaft showing the configuration of the cylindrical body exemplified in another embodiment [8]. It is a side view of the cylindrical body which shows the structure of the cylindrical body illustrated in another embodiment [8]. It is a cross-sectional plan view of the periphery of the right end part of the drive shaft which shows the structure of the cylindrical body illustrated in another embodiment [13].

  Hereinafter, as an example of an embodiment for carrying out the present invention, an embodiment in which a fertilizer application apparatus that is an example of an agricultural supply apparatus according to the present invention is provided in a riding rice transplanter that is an example of a paddy field work machine will be described with reference to the drawings. To do.

The direction indicated by the arrow F shown in FIG. 1 is the front side of the riding rice transplanter, and the direction indicated by the arrow U is the upper side of the riding rice transplanter.
2 is the front side of the riding rice transplanter, and the direction indicated by the arrow R is the right side of the riding rice transplanter.

  As shown in FIGS. 1 and 2, the riding rice transplanter exemplified in the present embodiment includes a traveling vehicle body 1 configured in a riding type four-wheel drive type. A parallel link type link mechanism 2 is connected to the rear lower portion of the traveling vehicle body 1 so as to be vertically swingable. Further, a seedling planting device 3 for four-row planting is connected to the rear lower part of the link mechanism 2 so as to be able to roll. On the other hand, as an example of the agricultural supply apparatus A, a four-way fertilizer application apparatus 4 for supplying granular fertilizer, which is an example of a supply to the field, to the field is disposed at the rear upper part of the traveling vehicle body 1. Thereby, the riding rice transplanter is configured to a four-row planting mid-mount fertilization specification capable of planting and fertilizing a maximum of four seedlings. And the raising / lowering cylinder 5 which raises / lowers the seedling planting apparatus 3 via the link mechanism 2 is provided in the rear part of the traveling vehicle body 1. A single-acting hydraulic cylinder is adopted as the lifting cylinder 5.

  As shown in FIGS. 1 to 3, the traveling vehicle body 1 includes an engine 7 and the like at the front portion of the vehicle body frame 6. Further, a boarding operation unit 8 and the like are provided on the rear side of the vehicle body frame 6. The body frame 6 is connected to the front frame 9 for mounting the engine, a transmission case (hereinafter referred to as a T / M case) 10 connected to the rear end portion of the front frame 9, and the rear end portion of the T / M case 10. A rear frame 11, a seat frame 12 connected to the upper end of the rear frame 11, and the like. The boarding driver 8 includes a steering wheel 13 for steering the front wheels, a boarding step 14, a driver seat 15, a rear step 16, and the like.

  As shown in FIGS. 1 and 3, the T / M case 10 includes a left and right front axle case 17 extending laterally outward from the left and right sides of the front side, and a rear and left side of the rear side. The left and right swing cases 18 are extended. In addition, left and right front wheels 19 are mounted on the extending ends of the left and right front axle cases 17 so as to be steerable and drivable. Further, left and right rear wheels 20 are drivably mounted on the extending ends of the left and right swing cases 18. The left and right swing cases 18 swing up and down with a transmission shaft 21 extending in the left and right direction extending from the T / M case 10 to the left and right swing cases 18. These free end sides are connected to the vehicle body frame 6 via the left and right suspension mechanisms 22.

  As shown in FIGS. 1 to 7, the rear frame 11 is connected to the rear end portion of the T / M case 10, so that the support portion 11 </ b> A of the rear frame 11 extending upward is located behind the T / M case 10. It is comprised so that it may be located in. And the rear step 16 provided in the rear upper part of the traveling vehicle body 1 is supported from below by the upper surface of the support portion 11A. The rear step 16 has a lateral width longer than the wheel interval of the left and right rear wheels 20. And the cover part 16A used also as the rear-wheel fender extended toward the boarding step 14 from the right and left front ends is integrally formed.

  The seat frame 12 is connected to the upper end portion of the rear frame 11 together with the rear step 16 and is disposed above the rear step 16. The seat frame 12 is arranged on the rear upper part of the traveling vehicle body 1 via the left and right cushion rubbers 23 and a position adjusting mechanism 24 that enables the position adjustment of the driver seat 15 in the longitudinal direction of the fuselage. Support. The position adjusting mechanism 24 includes a left and right support shaft 25 that is detachably provided at the front end of the seat frame 12, a left and right bracket 26 that is provided on the driver seat 15, and the like. Then, three through holes 26A for inserting the support shafts are formed in the left and right brackets 26 at predetermined intervals in the front-rear direction, so that the position of the driver seat 15 can be adjusted in three stages in the front-rear direction. ing. Further, it is possible to perform a swinging operation over the use position of the driver seat 15 with the support shaft 25 as a fulcrum and the forward lying position.

  As shown in FIG. 1, the power from the engine 7 is transmitted to a hydrostatic continuously variable transmission 28 provided as a main transmission via a belt tension type main clutch 27 and the like. The power after the shift by the hydrostatic continuously variable transmission 28 is branched into first power and second power inside the T / M case 10. The first power is transmitted to a gear-type auxiliary transmission (not shown) built in the T / M case 10. Then, the first power after the shift by the auxiliary transmission is branched into traveling and fertilizer application inside the T / M case 10. The traveling power is branched into front wheel driving and rear wheel driving inside the T / M case 10. Power for driving the front wheels is transmitted to the left and right front wheels 19 via a front wheel transmission system (not shown). Further, power for driving the rear wheels is transmitted to the left and right rear wheels 20 via a rear wheel transmission system (not shown). The power for fertilizing is transmitted to the fertilizing device 4 via a fertilizing clutch (not shown) built in the T / M case 10. The second power is transmitted to the seedling planting device 3 for seedling planting through a gear-type inter-strain transmission (not shown) and a planting clutch (not shown) incorporated in the T / M case 10. ing. The planting clutch is linked to the fertilization clutch so that the fertilization clutch is similarly intermittently operated in conjunction with the intermittent operation.

  As shown in FIGS. 1 and 2, the seedling planting device 3 includes a four-row leveling float 30, a four-row seedling platform 31, a power distribution mechanism 32, a lateral feed mechanism 33, and four planting mechanisms. 34 and a vertical feed mechanism 35 for four strips.

  The leveling float 30 slides while leveling the mud surface of the farm field as the traveling vehicle body 1 travels during work traveling. The seedling stage 31 is formed so as to place a maximum of four mat-like seedlings. The power distribution mechanism 32 distributes and supplies the power from the traveling vehicle body 1 to the lateral feed mechanism 33, each planting mechanism 34, and each vertical feed mechanism 35. The lateral feed mechanism 33 reciprocates the seedling stage 31 with a constant stroke in the left-right direction by the power from the power distribution mechanism 32. Each planting mechanism 34 cuts a predetermined amount of planted seedlings from the lower end of the mat-like seedling that reciprocates in the left-right direction together with the seedling mount 31 by the power from the power distribution mechanism 32 and after leveling by the leveling float 30. Plant in the field mud. Each vertical feed mechanism 35 feeds a corresponding mat-like seedling vertically toward the lower end of the seedling stage 31 at a predetermined pitch by the power from the power distribution mechanism 32 every time the seedling stage 31 reaches the left and right stroke ends. To do. And by these operation | movement, the seedling planting apparatus 3 is comprised for 4 articles | strands which can plant a maximum of 4 seedlings.

  As shown in FIGS. 1 to 6, the fertilizer application device 4 includes a fertilizer frame 36, a fertilizer storage hopper 37, left and right feeding mechanisms 38, four fertilizer hoses 39, four groovers 40, and an electric motor A blower 41 is provided. And it arrange | positions to the aircraft body rear side of the driver's seat 15 in the rear part of the traveling vehicle body 1. FIG.

  The fertilizer application frame 36 is configured by bolting a left and right main member 42 that supports the left and right feeding mechanism 38 from the rear and a left and right auxiliary member 43 that supports the left and right feeding mechanism 38 from the front. .

  The hopper 37 is formed in a horizontally long shape for storing 6 pieces of granular fertilizer. The hopper 37 is arranged at the rear upper part of the traveling vehicle body 1 together with the feeding mechanisms 38 and the blowers 41 in such an arrangement that the left and right centers thereof coincide with the left and right centers of the airframe. At the lower end portion of the hopper 37, three discharge portions 37A are provided at predetermined intervals in the left-right direction. Then, the granular fertilizer is prevented from flowing into the discharge portion 37A located on the left and right center side of the hopper 37 inside the hopper 37, and the granular fertilizer is guided to flow down to the discharge portion 37A located on the left and right ends of the hopper 37. A guide member 44 is detachably provided. In other words, the specification of the hopper 37 for six strips is changed to that for four strips by mounting the guide member 44 on the hopper 37 for six strips.

  The left and right feeding mechanisms 38 are connected at their upper ends to discharge portions 37 </ b> A located on the left and right ends of the hopper 37. The left and right feeding mechanisms 38 are connected by a fertilizer application frame 36. The left and right feeding mechanisms 38 are provided with feeding rolls 45 that are rotated by fertilizing power from the traveling vehicle body 1. Then, from the plurality of recesses 45A provided in the left half of each feeding roll 45 and the plurality of recesses 45A provided in the right half, by the rotation of each feeding roll 45, two pieces of granular fertilizer from the inside of the hopper 37 Is configured for two items that are fed downward by a predetermined amount. Thereby, it is set as the structure which pays out the granular fertilizer for a maximum of four strips.

  Each fertilization hose 39 has one end thereof connected to the corresponding feeding mechanism 38. In addition, a grooving device 40 is connected to the other end of each fertilization hose 39. Thereby, each fertilization hose 39 guides the granular fertilizer which each delivery mechanism 38 paid out to the corresponding groove making machine 40. FIG.

  Each grooving device 40 is arranged and set at a position adjacent to the corresponding planting mechanism 34 in the lateral direction of the machine body and attached to the leveling float 30. And each grooving machine 40 forms the groove | channel for fertilization in the mud part of a farm field with the driving | running | working of the traveling vehicle body 1 at the time of work driving | running | working, and burys granular fertilizer in the groove | channel.

  The blower 41 is bolted to the left end portion of the fertilization frame 36. The blower 41 is operated by the electric power from the traveling vehicle body 1, thereby generating a conveying wind from each feeding mechanism 38 to each grooving device 40 through the fertilizer hose 39. Thereby, the flow in each fertilization hose of the granular fertilizer which each delivery mechanism 38 paid out can be made smooth.

  As shown in FIGS. 1 to 8, the fertilizer application device 4 includes a left and right drive shaft 48 extending across the left and right feed mechanism 38, a feed transmission mechanism 49 that transmits the power for fertilization from the traveling vehicle body 1 to the drive shaft 48, and The feeding amount adjusting mechanism 50 that enables the batch adjustment of the fertilizer feeding amount by each feeding mechanism 38 is provided.

  The drive shaft 48 is configured by a hexagonal shaft having a regular hexagonal cross section. The drive shaft 48 is externally fitted with two output gears 52 that mesh with and interlock with the input gears 51 provided in the respective feeding mechanisms 38. Further, the drive shaft 48 is externally equipped with two fertilizer application number switching clutches 53 for intermittently transmitting power from the drive shaft 48 to the corresponding output gear 52. Each fertilization line number switching clutch 53 is linked to two line number switching levers 54 provided in the boarding operation unit 8 via two fertilization line number switching operation systems 55. Thereby, each fertilizer application | coating number switching clutch 53 enables the intermittent operation by the corresponding number switching switch 54. FIG.

  On the other hand, the seedling planting device 3 includes two planting line number switching clutches 56 that intermittently transmit power from the power distribution mechanism 32 to the corresponding two planting mechanisms 34, and two vertical channels that correspond from the power distribution mechanism 32. Two longitudinal feed number switching clutches 57 for intermittently transmitting power to the feed mechanism 35 are provided. Each planting number switching clutch 56 is linked to the corresponding number switching lever 54 through two planting number switching operation systems 58. Thereby, each planting number switching clutch 56 enables intermittent operation by the corresponding number switching lever 54. Each longitudinal feed number switching clutch 57 is linked to the corresponding number switching lever 54 via two longitudinal feed number switching operation systems 59. Thereby, each vertical feed number switching clutch 57 enables intermittent operation by the corresponding number switching lever 54.

  From the above configuration, by operating each row number switching lever 54, the working state of this riding rice transplanter is operated by all the planting mechanisms 34 and the vertical feed mechanism 35 in the seedling planting device 3, and the fertilizer 4 for operating all the feeding mechanisms 38 in 4, operating the planting mechanism 34 and the longitudinal feed mechanism 35 for the left two strips in the seedling planting device 3, and the left feeding mechanism in the fertilizer application device 4. The right side of the left two-row working state that operates 38, the right two-row planting mechanism 34 and the vertical feed mechanism 35 in the seedling planting device 3 are operated, and the right feeding mechanism 38 in the fertilizer application device 4 is operated. Select the two-row working state or the all-row stop state in which all the planting mechanisms 34 and the vertical feed mechanisms 35 in the seedling planting device 3 are stopped and all the feeding mechanisms 38 in the fertilizer application device 4 are stopped. Switch to one It is possible.

  As shown in FIGS. 5, 6, 8, and 9, the fertilizer application device 4 includes a fertilizer stop switching lever 60 that collectively switches the feeding mechanisms 38 to a stopped state. The switching lever 60 is provided at the right end of the fertilizer application frame 36 so as to be able to switch between a stop position and a stop release position. The switching lever 60 is linked to each fertilization line number switching clutch 53 via a fertilization state switching operation system 62 including a left-right linking member 61 and the like. Accordingly, each feeding mechanism 38 is configured to be switched to the stopped state regardless of the operation position of each number switching lever 54 with the swinging operation of the switching lever 60 from the stop release position to the stop position. . Further, as the switching lever 60 swings from the stop position to the stop release position, each feeding mechanism 38 is configured to switch to an operating state corresponding to the operation position of the corresponding number switching lever 54. .

  That is, by swinging the switching lever 60 for stopping fertilization, the working state of the riding rice transplanter is changed to a planting fertilization state in which seedling planting device 3 performs seedling planting and fertilizer device 4 fertilization, and fertilizer application device. It is possible to switch to a planting state in which only seedling planting by the seedling planting apparatus 3 is performed without performing fertilization according to 4.

  As shown in FIGS. 1, 3 to 5, and FIGS. 9 to 18, the feeding transmission mechanism 49 outputs the fertilization power take-out shaft 63 facing left and right provided on the left side of the T / M case 10 as power for fertilization. A first conversion unit 64 that converts the rotational power to be reciprocated into a reciprocating oscillating motion; and a second conversion unit 65 that converts the reciprocating oscillating motion into a positive rotational motion of the drive shaft 48. And the 2nd conversion part 65 linked with the feed amount adjustment mechanism 50 mentioned above is arranged with the feed amount adjustment mechanism 50 in the right end part of the body.

  The first converter 64 includes a connecting rod 67 whose one end is pin-connected to a rotating arm 66 that rotates integrally with the fertilization power take-off shaft 63, a first arm 68 that is pin-connected to the other end of the connecting rod 67, and a first arm 68. And a second arm 70 secured to the right end of the linkage shaft 69 so as to swing integrally with the first arm 68 via the linkage shaft 69. Yes. And by these, the 1st conversion part 64 has converted the rotational power from the fertilizer power extraction shaft 63 into the reciprocating rocking motion of the 1st arm 68 and the 2nd arm 70.

  The drive shaft 48 is equipped with a one-way clutch 71 for preventing reverse rotation that prevents reverse rotation of the drive shaft 48 at its rightmost end. The one-way clutch 71 for preventing reverse rotation has its outer ring 71A fixed to the main member 42 of the fertilizer frame 36 by bolts.

  The second converter 65 is a first one-way clutch 72 and a second one-way clutch 73 for forward rotation operation that enables forward rotation operation of the drive shaft 48, and the second arm 70 in the forward direction of the first converter 64 is swung in the forward direction. The first link mechanism 74 that transmits the dynamic motion (the swinging motion to the rear of the machine body) to the drive shaft 48 as the positive rotational power of the drive shaft 48 via the first left one-way clutch 72 and the first conversion unit 64. A second link mechanism 75 that transmits the swinging motion of the two arms 70 in the backward direction (swinging motion forward of the machine body) to the driving shaft 48 as the positive rotational power of the driving shaft 48 via the second one-way clutch 73 on the right side, etc. It has.

  The first one-way clutch 72 and the second one-way clutch 73 are externally fitted to the right end portion of the drive shaft 48 in a state of being arranged side by side at a position on the inner side of the body relative to the one-way clutch 71 for preventing reverse rotation.

  The first link mechanism 74 includes a turnbuckle-type connecting rod 76 whose one end is pin-connected to the second arm 70, a swing member 77 pin-connected to the other end of the link rod 76, and one end of the swing member 77. The first linkage member 78 is pin-coupled, and the first swing link 79 is pin-coupled to the other end of the first linkage member 78.

  The second link mechanism 75 includes a linkage rod 76 and a swing member 77 shared with the first link mechanism 74, a second link member 80 having one end connected to the swing member 77, and a second link member 80. The second swing link 81 is connected to the end by a pin.

  The first swing link 79 has a base end fixed to the outer ring 72 </ b> A of the first one-way clutch 72. The base end of the second swing link 81 is fixed to the outer ring 73 </ b> A of the second one-way clutch 73. As a result, the second linkage member 80 and the second swing link 81 of the second link mechanism 75 are located on the right outer side of the airframe relative to the first linkage member 78 and the first swing link 79 of the first link mechanism 74. It is configured as follows.

  The second link mechanism 75 is configured to be switchable between a transmission state that transmits to the drive shaft 48 and a transmission stop state that stops transmission. With this configuration, when the second link mechanism 75 is switched to the transmission state, the forward swinging motion and the backward swinging motion of the second arm 70 in the first conversion unit 64 are performed via the second conversion unit 65. This can be transmitted as the positive rotational power of the drive shaft 48. Thereby, the rotation angle of the feeding roll 45 in each feeding mechanism 38 obtained from the reciprocating swing of the second arm 70 can be increased, and each of the feeding mechanisms 38 per one reciprocating swing of the second arm 70. Fertilizer feed amount can be increased. On the other hand, when the second link mechanism 75 is switched to the transmission stop state, only the forward swinging motion of the second arm 70 in the first conversion unit 64 is transferred to the forward rotation power of the drive shaft 48 via the second conversion unit 65. Can be communicated as. Thereby, the rotation angle of the feeding roll 45 in each feeding mechanism 38 obtained from the reciprocating swing of the second arm 70 can be reduced, and each of the feeding mechanisms 38 per one reciprocating swing of the second arm 70 can be reduced. Fertilizer feed amount can be reduced.

  That is, by switching the second link mechanism 75 between the transmission state and the transmission stop state, the fertilizer feeding state of each feeding mechanism 38 is set to the standard amount of the fertilizer feeding amount per one reciprocating swing of the second arm 70. It is possible to switch between the first feeding state and the second feeding state in which the fertilizer feeding amount per one reciprocating swing of the second arm 70 is less than the standard amount, and the operating state of the fertilizer application device 4 is changed to the standard amount of fertilization. It can switch to the standard fertilization state to perform and the weight reduction fertilization state to perform fertilization with less fertilization amount than a standard amount.

  As shown in FIGS. 2, 4 to 6, and FIGS. 9 to 18, the feed amount adjustment mechanism 50 includes a front and rear screw shaft 82 that can swing up and down, and a human operation handle 83 that is fixed to the front end of the screw shaft 82. And a linkage arm 84 that links the screw shaft 82 to the swinging member 77 of the second conversion portion 65.

  Then, when the handle 83 is rotated in the decreasing direction, the linkage arm 84 is oscillated and displaced in the declining direction by the screw feeding action by the screw shaft 82, and along with this oscillating displacement, the oscillating member of the second converter 65. 77 is oscillated and displaced in the decreasing direction. As a result, the bending of the oscillating links 79 and 81 and the linking members 78 and 80 that link the oscillating member 77 and the one-way clutches 72 and 73 for forward rotation operation becomes shallow, and the oscillating angle of the oscillating member 77 is reduced. The swing angle of the swing links 79 and 81 with respect to is reduced. As a result, the fertilizer feed amount by each feed mechanism 38 of the fertilizer applicator 4 can be reduced collectively.

  On the contrary, when the handle 83 is rotated in the increasing direction, the linkage arm 84 is oscillated and displaced in the increasing direction by the screw feeding action by the screw shaft 82, and the oscillation of the second conversion portion 65 is accompanied by this oscillating displacement. The member 77 is oscillated and displaced in the increasing direction. As a result, the bending of the linking members 78 and 80 and the oscillating links 79 and 81 linking the oscillating member 77 and the one-way clutches 72 and 73 for forward rotation operation becomes deep, and the oscillating angle of the oscillating member 77 is increased. The swing angle of the swing links 79 and 81 with respect to the is increased. As a result, the fertilizer feed amount by each feed mechanism 38 of the fertilizer applicator 4 can be increased collectively.

  That is, the feed amount adjustment mechanism 50 is configured as a screw feed adjustment type that adjusts the fertilizer feed amount by each feed mechanism 38 steplessly in a batch by the screw feed action of the screw shaft 82.

  The 2nd conversion part 65 is the case where each fertilizer delivery amount in the reduced amount fertilization state of the fertilizer application device 4 when the fertilizer feed amount of each feed mechanism 38 in the standard fertilization state of the fertilizer applicator 4 is set to the minimum by the feed amount adjustment mechanism 50 When the fertilizer feed amount of the mechanism 38 is set to the maximum by the feed amount adjusting mechanism 50, the rotation of the drive shaft 48 in the positive rotation direction with respect to one reciprocating swing of the second arm 70 in the first conversion unit 64 is performed. The link ratio of the first link mechanism 74 and the second link mechanism 75 is set so that the corners are the same and the fertilizer feed amount of each feed mechanism 38 is the same.

  Thereby, in the adjustment area | region of the fertilizer feed amount by the feed amount adjustment mechanism 50 in the standard fertilization state of the fertilizer application apparatus 4, and the adjustment area | region of the fertilizer feed amount by the feed amount adjustment mechanism 50 in the reduced weight fertilization state of the fertilizer application apparatus 4, It prevents the useless adjustment area | region where the fertilizer feed amount overlaps existing. As a result, the adjustment of the fertilizer feed amount by the feed amount adjusting mechanism 50 using the switching between the standard fertilization state and the reduced weight fertilization state of the fertilizer application device 4 can be performed satisfactorily by a wide and wide range of adjustments without waste.

  As shown in FIGS. 9 and 11 to 13, the one-way clutch 71 for preventing reverse rotation includes a connecting portion 71 </ b> B for the main member 42 of the fertilization frame 36 on the outer ring 71 </ b> A. The main member 42 of the fertilizer application frame 36 includes a connecting portion 42 </ b> A that enables bolt connection with the connecting portion 71 </ b> B of the one-way clutch 71. Two stepped bolts 103, two washers 104, and two spring washers 105 are used to connect the connecting portion 42 </ b> A of the main member 42 and the connecting portion 71 </ b> B of the one-way clutch 71. Then, the hole diameter in the connecting portion 71B of the one-way clutch 71 is made larger than the large-diameter portion 103A of the stepped bolt 103, and the connecting portion 71B of the one-way clutch 71 is connected to the connecting portion 42A of the main member 42 and the stepped bolt 103. It is configured so as to be sandwiched and held via a washer 104 and a spring washer 105 between the head 103 </ b> B.

  As shown in FIGS. 1 to 3, 5, 6, and 9 to 19, the riding rice transplanter uses the power for fertilization from the traveling vehicle body 1 as a transmission for transmission including three one-way clutches 71 to 73. This is transmitted to the drive shaft 48 via the mechanism 49. The three one-way clutches 71 to 73 are externally fitted between the left and right C-shaped retaining rings 100 engaged and equipped at the right end of the drive shaft 48 in a state of being arranged in the left-right direction. And the spacer 101 is interposed between the adjacent one-way clutches 71-73.

  As shown in FIGS. 12, 13, and 19 to 22, each one-way clutch 71 to 73 includes inner rings 71 </ b> C to 73 </ b> C that are externally fitted to the drive shaft 48. Each inner ring 71 </ b> C to 73 </ b> C has small-diameter portions 71 </ b> Cb to 73 </ b> Cb having regular hexagonal fitting holes 71 </ b> Ca to 73 </ b> Ca similar to the cross section of the drive shaft 48, and round holes 71 </ b> Cc to 73 </ b> Cc larger in diameter than the circumscribed circle of the drive shaft 48. Expanded diameter portions 71Cd to 73Cd are provided. In each one-way clutch 71 to 73, the small diameter portions 71Cb to 73Cb of the inner rings 71C to 73C are fitted into the outer rings 71A to 73A, and the enlarged diameter portions 71Cd to 73Cd of the inner rings 71C to 73C are respectively connected to the outer rings 71A to 73A. It is configured to protrude outward. Each of the inner rings 71C to 73C has an outer diameter of the enlarged diameter portions 71Cd to 73Cd and the outer diameter of the oil seal 102 interposed between the outer rings 71A to 73A of the one-way clutches 71 to 73 and the inner rings 71C to 73C. They are formed so as to have approximately the same size.

  The feeding transmission mechanism 49 includes a resin-made cylindrical body 110 that is press-fitted between the enlarged diameter portions 71 </ b> Cd to 73 </ b> Cd of the inner rings 71 </ b> C to 73 </ b> C provided in the one-way clutches 71 to 73 and the drive shaft 48. Then, each cylindrical body 110 is press-fitted between the drive shaft 48 and the enlarged diameter portions 71Cd to 73Cd of the inner rings 71C to 73C, thereby causing individual differences between the drive shaft 48 and the one-way clutches 71 to 73. The backlash between the drive shaft 48 and each of the inner rings 71C to 73C that may occur due to the backlash can be eliminated, and the drive shaft 48 and the one-way clutches 71 to 73 generated due to the backlash can be eliminated. Transmission loss can be eliminated.

  Thereby, when manufacturing a plurality of riding rice transplanters, the power from the traveling vehicle body 1 is the same, but due to the transmission loss that occurs between the drive shaft 48 and the one-way clutches 71 to 73. In addition, for each fertilizer application device 4 provided in each riding rice transplanter, it is possible to avoid a possibility that a difference occurs in the rotational speed of the drive shaft 48 obtained through the three one-way clutches 71 to 73.

  As a result, it is possible to avoid a possibility that the amount of fertilizer fed from the fertilizer application device 4 provided in each riding rice transplanter may be different depending on the fertilizer application device 4 provided in each riding rice transplanter.

  Further, the inner rings 71C to 73C of the respective one-way clutches 71 to 73 include the small diameter portions 71Cb to 73Cb and the enlarged diameter portions 71Cd to 73Cd described above, for example, to expand the diameter of the inner rings 71C to 73C. Compared with the case where the cylindrical body 110 having the entire length of each of the inner rings 71C to 73C is press-fitted between the drive shaft 48 and each of the inner rings 71C to 73C, the one-way clutches 71 to 73 in the radial direction. An increase in size can be suppressed.

  Moreover, by pressing the cylindrical bodies 110 between the drive shaft 48 and the enlarged diameter portions 71Cd to 73Cd of the inner rings 71C to 73C, the contact area between the inner rings 71C to 73C and the cylindrical bodies 110 is increased. can do. Thereby, generation | occurrence | production of the slip between the inner ring | wheel 71C-73C of each one-way clutch 71-73 and each cylindrical body 110 can be suppressed effectively, and inner ring | wheel 71C-73C of each one-way clutch 71-73, Generation | occurrence | production of the transmission loss resulting from the slip between each cylindrical body 110 can be suppressed effectively.

  By the way, for example, when the cylindrical body 110 is constituted by a single cylindrical member, when the cylindrical body 110 is press-fitted between the drive shaft 48 and the enlarged diameter portions 71Cd to 73Cd of the inner rings 71C to 73C, It is necessary to slide the cylindrical body 110 from the right end portion of the drive shaft 48 to the press-fitting location after the cylindrical body 110 is fitted on the right end portion of the drive shaft 48. Therefore, it takes time to press-fit the cylindrical body 110 between the drive shaft 48 and each of the inner rings 71C to 73C. Further, during the sliding movement of the cylindrical body 110, the inner peripheral surface of the cylindrical body 110 is inserted into the corner portion 48A of the drive shaft 48, the engagement groove 48C for the retaining ring formed on the drive shaft 48, or the like. There is a risk of being damaged by sliding contact.

  Therefore, as shown in FIGS. 20 to 22, the two curved members are arranged so that each cylindrical body 110 is sandwiched between two opposing corners 48 </ b> A of the drive shaft 48 with respect to the drive shaft 48 having a regular hexagonal cross section. 111 is formed into a cylindrical shape.

  Accordingly, it is troublesome to externally fit the cylindrical body 110 to the right end portion of the drive shaft 48 by press-fitting each curved member 111 between the drive shaft 48 and the enlarged diameter portions 71Cd to 73Cd of the inner rings 71C to 73C. In addition, without the need to slide and move the cylindrical body 110 from the right end portion of the drive shaft 48 to the press-fitted location, the cylindrical body 110 is connected to the drive shaft 48 and the enlarged diameter portions 71Cd to 73Cd of the inner rings 71C to 73C. It can be pressed in between.

  Further, since it is not necessary to slide the cylindrical body 110 in a state of being externally fitted to the drive shaft 48, the inner peripheral surface 110A of the cylindrical body 110 is driven by the drive shaft during the sliding movement of the cylindrical body 110. It is possible to avoid the risk of being damaged due to sliding contact with the corner portion 48A of 48 or the engaging groove 48C for the retaining ring formed on the drive shaft 48.

  As shown in FIGS. 20 to 22, each bending member 111 includes an inner surface 111 </ b> A along the outer peripheral surface 48 </ b> B of the drive shaft 48 and an outer surface 111 </ b> B that curves along the inner peripheral surfaces 71 </ b> Ce to 73 </ b> Ce of the respective enlarged diameter portions 71 </ b> Cd to 73 </ b> Cd. It has. The inner peripheral surface 110A of the cylindrical body 110 is formed by the inner surfaces 111A of the two bending members 111 that form a pair. Further, the outer peripheral surface 110B of the cylindrical body 110 is formed by the outer surfaces 111B of the two bending members 111 that form a pair.

  Each of the bending members 111 includes three protrusions 111C extending in the axial direction of the drive shaft 48 at positions away from the portions facing the corners 48A of the drive shaft 48 on their outer surfaces 111B. Further, the inner surface 111A of each bending member 111 is formed by three planar portions 111Aa that are in surface contact with three of the six planar portions 48Ba that form the outer peripheral surface 48B of the drive shaft 48.

  In other words, by providing the outer surface 111B of each bending member 111 with three protrusions 111C extending in the axial direction of the drive shaft 48, between the drive shaft 48 and the enlarged diameter portions 71Cd to 73Cd of the inner rings 71C to 73C. It becomes easy to press-fit each bending member 111 into the. Then, when each bending member 111 is press-fitted between the drive shaft 48 and the enlarged diameter portions 71Cd to 73Cd of the inner rings 71C to 73C, the protrusions 111C provided on the outer surface 111B of each bending member 111 become the inner rings 71C to 73C. The three flat portions 111Aa forming the inner surface 111A of each bending member 111 are pushed out toward the drive shaft as the inner diameter surfaces 71Ce to 73Ce of the enlarged diameter portions 71Cd to 73Cd are pressed against each other. It comes in close contact with the six plane portions 48Ba forming the outer peripheral surface 48B of the 48.

  As a result, individual differences between the drive shaft 48 and the one-way clutches 71 to 73 are facilitated while facilitating the press-fitting of the curved members 111 between the drive shaft 48 and the enlarged diameter portions 71Cd to 73Cd of the inner rings 71C to 73C. The backlash between the drive shaft 48 and the inner rings 71C to 73C that may be caused can be more reliably eliminated.

  In addition, since the three plane portions 111Aa forming the inner surface 111A of each bending member 111 have an included angle of 120 degrees, each bending member 111 has a draft of 30 degrees on the inner surface 111A. . Thereby, it is possible to facilitate die cutting after molding each bending member 111 without providing a dedicated draft on the inner surface side of each bending member 111.

  As shown in FIG. 22, each protrusion 111 </ b> C of each bending member 111 has both ends 111 </ b> Ca in the axial direction of the drive shaft 48 extending outward toward the both ends in the axial direction of the drive shaft 48. It is inclined in a state where the protruding amount is small.

  As a result, when the curved members 111 are press-fitted between the drive shaft 48 and the enlarged diameter portions 71Cd to 73Cd of the inner rings 71C to 73C, the drive shaft 48 and the inner rings 71C to 71C are irrelevant to the directions of the curved members 111. It is possible to make it easier to press-fit each bending member 111 between the 73C diameter-expanded portions 71Cd to 73Cd.

  [Another embodiment]

[1] Agricultural supply device A, for example, a seedling planting device provided with a one-way clutch for vertical seedling feeding that transmits power from traveling vehicle body 1 to a drive shaft for vertical seedling feeding, and power from traveling vehicle body 1 Direct seeding device equipped with a one-way clutch for seed feeding that transmits to a drive shaft for seed feeding, or medicine spraying equipped with a one-way clutch for medicine feeding that transmits the power from the traveling vehicle body 1 to the driving shaft for drug delivery It may be a device.

[2] The number of working strips of the agricultural supply apparatus A may be five or more, for example. The number of the one-way clutches 71 to 73 included in the agricultural supply apparatus A can be variously changed according to the type or configuration of the agricultural supply apparatus A. For example, the agricultural supply apparatus A may be provided with a single one-way clutch 72.

[3] The configuration of the traveling vehicle body 1 can be variously changed. For example, the traveling vehicle body 1 may be configured to include a fixed rear axle case instead of the left and right swing cases 18. The traveling vehicle body 1 may be configured to include the engine 7 below the driver seat 15.

[4] The angular axis employed for the drive shaft 48 can be variously changed. For example, a square axis such as a square, regular pentagon, or regular octagon may be adopted as the drive shaft 48.

[5] The inner rings 71C to 73C of the one-way clutches 71 to 73 have round holes 71Cc to 73Cc larger in diameter than the circumscribed circle of the drive shaft 48 over the entire length of the inner rings 71C to 73C in the axial direction of the drive shaft 48. The cylindrical body 110 may be configured to be press-fitted between the drive shaft 48 and the inner rings 71C to 73C over the entire length of the inner rings 71C to 73C in the axial direction of the drive shaft 48.

[6] The inner rings 71C to 73C of the one-way clutches 71 to 73 are formed so as to have enlarged diameter portions 71Cd to 73Cd at both ends of the inner rings 71C to 73C, and both ends (expanded) of the drive shaft 48 and the inner rings 71C to 73C. You may comprise so that the cylindrical body 110 may be press-fit between diameter part 71Cd-73Cd).

[7] As shown in FIGS. 23 to 25, the inner peripheral surface 110 </ b> A of the cylindrical body 110 (the inner surface 111 </ b> A of the bending member 111) is provided with three protrusions 111 </ b> C extending in the axial direction of the drive shaft 48. The outer periphery of the body 110 (the outer surface 111B of the bending member 111) has the same shape as the inner periphery of the inner rings 71C to 73C provided in the one-way clutches 71 to 73, and can come into surface contact with the inner peripheral surfaces 71Ce to 73Ce of the inner rings 71C to 73C. In the press-fitted state of the cylindrical body 110 (curved member 111) formed, each of the protrusions 111C presses against the outer peripheral surface 48B of the drive shaft 48, and the outer peripheral surface 110B of the cylindrical body 110 (the outer surface of the curved member 111). 111B) may be configured to be in pressure contact with the inner peripheral surfaces 71Ce to 73Ce of the inner rings 71C to 73C. Then, the protrusions 111C of the cylindrical body 110 (the bending member 111) are arranged so that the both end portions 111Ca in the axial direction of the drive shaft 48 are outward toward the both end sides in the axial direction of the drive shaft 48. You may form so that it may incline in the state where protrusion amount decreases.

[8] As shown in FIGS. 26 and 27, the inner peripheral surface 110A of the cylindrical body 110 (the inner surface 111A of the bending member 111) is provided with two protrusions 111C extending in the axial direction of the drive shaft 48. The outer periphery of the cylindrical body 110 (the outer surface 111B of the bending member 111) can be in surface contact with the inner peripheral surfaces 71Ce to 73Ce of the inner rings 71C to 73C with the same shape as the inner periphery of the inner rings 71C to 73C provided in the one-way clutches 71 to 73. In the press-fitted state of the cylindrical body 110 (curved member 111), each of the protrusions 111C presses against the corner portion 48A of the drive shaft 48, and the outer peripheral surface 110B of the cylindrical body 110 has the inner rings 71C to 73C. You may comprise so that it may press-contact to inner peripheral surface 71Ce-73Ce. And although illustration is abbreviate | omitted, also in this structure, both ends 111Ca in the axial center direction of those drive shafts 48 are each shaft 111C of the cylindrical body 110 (bending member 111). You may form so that it may incline in the state in which the amount of protrusions to the outside decreases toward both ends in the center direction.

[9] Each protrusion 111 </ b> C provided in the cylindrical body 110 (bending member 111) has an end portion in the axial direction of the drive shaft 48 only outward toward the one end side in the axial direction of the drive shaft 48. You may form so that it may incline in the state where the amount of protrusion to decreases. Further, each protrusion 111C may be formed so that the outward protrusion amount is constant over both ends of the drive shaft 48 in the axial direction.

[10] The number and arrangement of the protrusions 111 </ b> C included in the cylindrical body 110 (the bending member 111) can be variously changed according to the cross-sectional shape of the drive shaft 48. For example, the drive shaft is provided at each of a portion of the outer peripheral surface 110B of the cylindrical body 110 (the outer surface 111B of the bending member 111) facing the corner portion 48A of the drive shaft 48 and a position away from the portion facing the corner portion 48A. A plurality of protrusions 111C extending in the axial direction of 48 may be provided. Further, driving is performed on each of the inner peripheral surface 110A of the cylindrical body 110 (the inner surface 111A of the bending member 111) facing the corner 48A of the drive shaft 48 and the position away from the facing portion of the corner 48A. A plurality of protrusions 111C extending in the axial direction of the shaft 48 may be provided.

[11] The cylindrical body 110 (curved member 111) is made up of an inner peripheral surface 110A of the cylindrical body 110 (inner surface 111A of the curved member 111) and an outer peripheral surface 110B of the cylindrical body 110 (outer surface 111B of the curved member 111). You may form so that it may have several protrusion 111C in both. In addition, the cylindrical body 110 (curved member 111) is composed of an inner peripheral surface 110A of the cylindrical body 110 (inner surface 111A of the curved member 111) and an outer peripheral surface 110B of the cylindrical body 110 (outer surface 111B of the curved member 111). You may form so that it may not have the protrusion 111C in any.

[12] The cylindrical body 110 may be constituted by a single cylindrical member. Further, the cylindrical body 110 may be formed into a cylindrical shape by three or more bending members 111.

[13] As shown in FIG. 28, a resin having a small-diameter portion 120A that is externally fitted to the drive shaft 48 in a press-contact state and a large-diameter portion 120B that is externally fit to the inner rings 71C to 73C of the one-way clutches 71 to 73. The cylindrical body 120 is provided, and is configured to eliminate rattling between the drive shaft 48 and the inner rings 71C to 73C caused by individual differences between the drive shaft 48 and the one-way clutches 71 to 73. May be.

  The present invention can be applied to agricultural supply devices such as a seedling planting device, a direct sowing device, a fertilizer application device, and a medicine spraying device that include a one-way clutch that transmits power from a traveling vehicle body to a drive shaft.

1 traveling vehicle body 48 drive shaft 48A corner portion 48B outer peripheral surface 71 one-way clutch 71C inner ring 71Ca fitting hole 71Cb small diameter portion 71Cc round hole 71Cd enlarged diameter portion 71Ce inner peripheral surface 72 one way clutch 72C inner ring 72Ca fitting hole 72Cb small diameter hole 72Cb 72Cd expanded diameter portion 72Ce inner peripheral surface 73 one-way clutch 73C inner ring 73Ca fitting hole 73Cb small diameter portion 73Cc round hole 73Cd expanded diameter portion 73Ce inner peripheral surface 110 cylindrical body 110A inner peripheral surface 110B outer peripheral surface 111 curved inner surface 111A inner surface portion 111A inner surface 111A 111C protrusion 111Ca both ends

Claims (9)

With a one-way clutch that transmits the power from the traveling vehicle body to the drive shaft,
The drive shaft is constituted by an angular axis having a polygonal cross section,
The one-way clutch includes an inner ring that is externally fitted to the drive shaft,
An agricultural supply apparatus in which a cylindrical body made of resin is press-fitted between the drive shaft and the inner ring. With a one-way clutch that transmits the power from the traveling vehicle body to the drive shaft,
The drive shaft is constituted by an angular axis having a polygonal cross section,
The one-way clutch includes an inner ring that is externally fitted to the drive shaft,
Press-fit a resin cylindrical body between the drive shaft and the inner ring,
The agricultural supply apparatus which comprises the said cylindrical body in the cylinder shape by the some bending member. With a one-way clutch that transmits the power from the traveling vehicle body to the drive shaft,
The drive shaft is constituted by an angular axis having a polygonal cross section,
The one-way clutch includes an inner ring that is externally fitted to the drive shaft,
The inner ring includes a small-diameter portion having a polygonal fitting hole that is the same as the cross-section of the drive shaft, and an enlarged-diameter portion having a round hole larger in diameter than a circumscribed circle of the drive shaft,
An agricultural supply apparatus in which a cylindrical body made of resin is press-fitted between the drive shaft and the enlarged diameter portion. With a one-way clutch that transmits the power from the traveling vehicle body to the drive shaft,
The drive shaft is constituted by an angular axis having a polygonal cross section,
The one-way clutch includes an inner ring that is externally fitted to the drive shaft,
The inner ring includes a small-diameter portion having a polygonal fitting hole that is the same as the cross-section of the drive shaft, and an enlarged-diameter portion having a round hole larger in diameter than a circumscribed circle of the drive shaft,
Press-fit a resin cylindrical body between the drive shaft and the enlarged diameter portion,
The agricultural supply apparatus which comprises the said cylindrical body in the cylinder shape by the some bending member. The inner periphery of the cylindrical body is formed in the same polygon as the cross-sectional shape of the drive shaft so as to be in surface contact with the outer peripheral surface of the drive shaft,
A plurality of ridges extending in the axial direction of the drive shaft at a position deviating from a portion facing the corner of the drive shaft on the outer peripheral surface of the cylindrical body;
2. In the press-fitted state of the cylindrical body, each of the protrusions is in pressure contact with the inner peripheral surface of the inner ring, and the inner peripheral surface of the cylindrical body is in pressure contact with the outer peripheral surface of the drive shaft. The agricultural supply apparatus as described in any one of -4. The inner periphery of the cylindrical body is formed in the same polygon as the cross-sectional shape of the drive shaft so as to be in surface contact with the outer peripheral surface of the drive shaft,
A plurality of ridges extending in the axial direction of the drive shaft at a position deviating from a portion facing the corner of the drive shaft on the outer peripheral surface of the cylindrical body;
In the press-fitted state of the cylindrical body, each of the protrusions presses against the inner peripheral surface of the inner ring, and the inner peripheral surface of the cylindrical body presses against the outer peripheral surface of the drive shaft,
The agricultural supply device according to any one of claims 1 to 4, wherein each of the protrusions is inclined at both ends in a state where the outward protrusion amount decreases toward both ends in the axial direction. . Provided with a plurality of protrusions extending in the axial direction of the drive shaft on the inner peripheral surface of the cylindrical body,
The outer periphery of the cylindrical body is formed in the same shape as the inner periphery of the inner ring so as to be in surface contact with the inner peripheral surface of the inner ring,
Each of the said protrusions press-contacts with the outer peripheral surface of the said drive shaft in the press-fit state of the said cylindrical body, and the outer peripheral surface of the said cylindrical body is press-contacted with the internal peripheral surface of the said inner ring | wheel. The agricultural supply apparatus according to any one of 4. Provided with a plurality of protrusions extending in the axial direction of the drive shaft on the inner peripheral surface of the cylindrical body,
The outer periphery of the cylindrical body is formed in the same shape as the inner periphery of the inner ring so as to be in surface contact with the inner peripheral surface of the inner ring,
In the press-fitted state of the cylindrical body, each of the protrusions presses against the outer peripheral surface of the drive shaft, and the outer peripheral surface of the cylindrical body presses against the inner peripheral surface of the inner ring,
The agricultural supply device according to any one of claims 1 to 4, wherein each of the protrusions is inclined at both ends in a state where the outward protrusion amount decreases toward both ends in the axial direction. . The drive shaft is a hexagonal shaft having a hexagonal cross section,
The cylindrical body is formed into a cylindrical shape by two curved members arranged in a state of sandwiching two opposite corners of the hexagonal shaft,
Each of the said bending members is an agricultural supply apparatus of Claim 2 or 4 provided with the inner surface which consists of a plane part of 3 surfaces which surface-contacts with the outer peripheral surface of the said drive shaft.

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